A multi-energy collaborative heating system, method, device and medium

Abstract

The application provides a multi-energy cooperative heating system, method, equipment and medium, and relates to the technical field of heating. The system comprises: a group of buried tube wells, which are used for transmitting external waste heat into a rock-soil layer to store heat and generate a heat storage rock-soil layer in a non-heating season; a biomass cogeneration unit, which is used for generating power, exhaust steam and flue gas; a ground source heat pump unit, which is used for extracting heat from the heat storage rock-soil layer in a heating season by taking a preset part of the power as a driving source, generating water at a first temperature according to the heat; a flue gas waste heat recovery device, which is used for recovering the flue gas and generating water at a second temperature by taking the flue gas as a driving source; and an absorption heat pump unit, which is used for increasing the temperature of the water at the first temperature and the water at the second temperature, generating water at a third temperature, and outputting the water at the third temperature to a heating pipe network. The application has the technical effect of meeting the long-term needs of a central heating pipe network for heating continuity and hot water quality.

Description

Technical Field

[0001] This application relates to the field of heating technology, specifically to a multi-energy coordinated heating system, method, equipment, and medium. Background Technology

[0002] District heating is a crucial infrastructure for ensuring the quality of life for residents in cold regions. However, with accelerated urbanization and the continued pursuit of "dual carbon" goals, the traditional fossil fuel-based district heating model faces significant challenges, including high energy consumption, high carbon emissions, and a single heat source structure. Meanwhile, a large amount of low-grade waste heat generated during industrial production and power generation is typically discarded during the off-season due to supply-demand mismatch, resulting in severe energy waste. Therefore, achieving efficient and coordinated utilization of multiple energy sources, cross-seasonal heat storage, and on-demand release have become critical technical challenges urgently needing to be addressed in the district heating sector.

[0003] To address the aforementioned technical issues, a common heating solution currently employed is a combination of biomass cogeneration and ground-source heat pumps. This involves using steam generated from biomass boiler combustion to drive a turbine for electricity generation, which in turn powers a ground-source heat pump to extract heat from shallow soil and rock layers. The heat is then upgraded using heat pump technology before being delivered to the centralized heating network, achieving a degree of cascaded development and utilization of renewable energy. While this solution reduces reliance on fossil fuels and lowers carbon emissions from the heating system, the ground-source heat pump's long-term unidirectional heat extraction from the soil and rock layers makes it difficult to maintain thermal balance. This leads to a continuous decline in soil temperature and a gradual decrease in the coefficient of performance (COP) of the ground-source heat pump units, making it difficult to guarantee long-term system heating stability. Furthermore, the multiple waste heat resources generated during biomass cogeneration are not fully recovered and utilized, resulting in a low overall energy utilization rate that fails to meet the long-term demands of centralized heating networks for continuous heating and high-quality hot water. Summary of the Invention

[0004] This application provides a multi-energy coordinated heating system, method, and equipment to meet the long-term requirements of centralized heating networks for heating continuity and hot water quality.

[0005] In a first aspect, this application provides a multi-energy coordinated heating system, the system comprising: a group of buried pipe wells, a biomass cogeneration unit, a ground source heat pump unit, a flue gas waste heat recovery device, and an absorption heat pump unit; wherein... The underground well network is used to connect with the heating end of an external waste heat source during the non-heating season, transferring the waste heat generated by the external waste heat source to the soil and rock layer for heat storage, forming a heat storage soil and rock layer; the biomass cogeneration unit is used to burn biomass fuel to generate electricity, exhaust steam, and flue gas, transmitting a predetermined portion of the electricity to the ground source heat pump unit and transmitting the exhaust steam to the absorption heat pump unit; the ground source heat pump unit is used to extract heat from the heat storage soil and rock layer during the heating season using a predetermined portion of the electricity as a driving source, generating water at a first temperature based on the heat, and then... Water at a certain temperature is fed into the absorption heat pump unit; the flue gas waste heat recovery device is used to recover flue gas, use the flue gas as a driving source to generate water at a second temperature, and feed the water at the second temperature into the absorption heat pump unit; the absorption heat pump unit is used to use the exhaust steam as a driving heat source, and use the water at the first temperature and the water at the second temperature as low-grade heat sources to heat the water at the first temperature and the water at the second temperature to generate water at a third temperature, and output the water at the third temperature to the heating network; wherein, the third temperature is higher than the first temperature and the second temperature.

[0006] By adopting the above technical solution, the buried well network is connected to the heating end of an external waste heat source during the non-heating season, continuously transferring external waste heat to the soil and rock layer for heat storage, forming a heat storage soil and rock layer. This effectively maintains the thermal balance of the soil and rock layer, ensuring the ability of the ground source heat pump unit to stably extract heat from the heat storage soil and rock layer during the heating season. This avoids the problem of the soil and rock layer temperature continuously decreasing due to long-term unidirectional heat extraction, which would lead to the degradation of the coefficient of performance of the ground source heat pump unit. During the heating season, the biomass cogeneration unit burns biomass fuel to simultaneously generate electricity, exhaust steam, and flue gas. A portion of the electricity is pre-set to drive the ground source heat pump unit to extract heat from the heat storage soil and rock layer. The system generates water at a first temperature, and the flue gas waste heat recovery device simultaneously recovers the flue gas to generate water at a second temperature, ensuring that multiple waste heat resources generated during biomass cogeneration are fully recovered and utilized. Furthermore, the absorption heat pump unit uses exhaust steam as the driving heat source and water at the first and second temperatures as low-grade heat sources to synergistically heat both, generating water at a third temperature higher than the first and second temperatures before outputting it to the heating network. This achieves cascaded quality improvement of multiple low-grade heat sources, significantly improving the overall energy utilization rate of the system, while simultaneously meeting the long-term requirements of centralized heating networks for heating continuity and hot water quality.

[0007] Secondly, this application provides a multi-energy coordinated heating method, the method comprising: during the non-heating season, transferring waste heat generated by an external waste heat source to a soil layer for heat storage, thereby generating a heat-storing soil layer; during the heating season, extracting heat from the heat-storing soil layer and generating water at a first temperature based on the heat; burning biomass fuel to generate flue gas, and using the flue gas as a driving source to generate water at a second temperature; using the water at the first temperature and the water at the second temperature as low-temperature heat sources to raise the temperature of the water at the first temperature and the water at the second temperature, thereby generating water at a third temperature, and outputting the water at the third temperature to the heating network; wherein the third temperature is higher than the first temperature and the second temperature.

[0008] Thirdly, this application provides an electronic device that adopts the following technical solution: it includes a processor, a memory, a user interface, and a network interface. The memory is used to store instructions, the user interface and the network interface are used to communicate with other devices, and the processor is used to execute the instructions stored in the memory to enable the electronic device to execute a computer program of any of the above-described multi-energy coordinated heating methods.

[0009] Fourthly, this application provides a computer-readable storage medium that stores a computer program capable of being loaded by a processor and executing any of the above-mentioned multi-energy coordinated heating methods.

[0010] In summary, this application includes at least one of the following beneficial technical effects: By connecting the underground well network to the heating end of an external waste heat source during the non-heating season, the external waste heat is continuously transferred to the soil and rock layer for heat storage, forming a heat storage soil and rock layer. This effectively maintains the thermal balance of the soil and rock layer and ensures the ability of the ground source heat pump unit to stably extract heat from the heat storage soil and rock layer during the heating season. This avoids the problem of the soil and rock layer temperature continuously decreasing due to long-term unidirectional heat extraction, which would lead to the degradation of the coefficient of performance of the ground source heat pump unit. During the heating season, the biomass cogeneration unit burns biomass fuel to simultaneously generate electricity, exhaust steam, and flue gas. A portion of the electricity is preset to drive the ground source heat pump unit to extract heat from the heat storage soil and rock layer to generate the first temperature. The waste heat recovery device simultaneously recovers water from the flue gas to generate water at a second temperature, ensuring full recovery and utilization of multiple waste heat resources generated during biomass cogeneration. Furthermore, the absorption heat pump unit uses exhaust steam as the driving heat source and water at the first and second temperatures as low-grade heat sources, synergistically heating both to generate water at a third temperature higher than the first and second temperatures before outputting it to the heating network. This achieves tiered quality improvement of multiple low-grade heat sources, significantly enhancing the overall energy utilization rate of the system while meeting the long-term requirements of centralized heating networks for continuous heating and high-quality hot water. Attached Figure Description

[0011] Figure 1 This is a schematic diagram of a multi-energy coordinated heating system provided in an embodiment of this application; Figure 2 This is a schematic flowchart of a multi-energy coordinated heating method provided in an embodiment of this application; Figure 3 This is a schematic diagram of the structure of an electronic device provided in an embodiment of this application.

[0012] Explanation of reference numerals in the attached drawings: 1. Evaporator; 2. Condenser; 3. Throttling device; 4. Compressor; 5. Generator; 6. Absorber; 7. Biomass boiler; 8. Steam turbine generator set; 9. Electric boiler; 10. Power plant waste heat; 11. Ground source heat pump unit; 12. Flue gas waste heat recovery device; 13. First absorption heat pump; 14. Second absorption heat pump; 15. Buried well group; 16. Thermal storage circulation pump; 17. Power plant waste heat heating circulation pump; 18. Electric boiler heating circulation pump; 19. Ground source heat pump evaporator circulation pump; 20. Ground source heat pump condenser circulation pump; 21. Absorption heat pump heating circulation pump; 22. Flue gas waste heat recovery circulation pump; 1000. Electronic equipment; 1001. Processor; 1002. Communication bus; 1003. User interface; 1004. Network interface; 1005. Memory. Detailed Implementation

[0013] To enable those skilled in the art to better understand the technical solutions in this specification, the technical solutions in the embodiments of this specification will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments.

[0014] In the description of the embodiments in this application, words such as "illustrative," "for example," or "for example" are used to indicate examples, illustrations, or explanations. Any embodiment or design described as "illustrative," "for example," or "for example" in the embodiments of this application should not be construed as being more preferred or advantageous than other embodiments or designs. Rather, the use of words such as "illustrative," "for example," or "for example" is intended to present the relevant concepts in a specific manner.

[0015] Based on the above method, this application also discloses a multi-energy coordinated heating system, comprising: a group of buried wells, a biomass cogeneration unit, a ground source heat pump unit, a flue gas waste heat recovery device, and an absorption heat pump unit; wherein... The underground well network is used to connect to the heating end of an external waste heat source during the non-heating season, transferring the waste heat generated by the external waste heat source to the soil and rock layer for heat storage, thus creating a heat storage soil and rock layer; the biomass cogeneration unit is used to burn biomass fuel to generate electricity, exhaust steam, and flue gas, transmitting a pre-set portion of the electricity to the ground source heat pump unit and transmitting the exhaust steam to the absorption heat pump unit; the ground source heat pump unit is used to extract heat from the heat storage soil and rock layer during the heating season, driven by a pre-set portion of the electricity, and generates a first temperature based on the heat. The system uses water at a first temperature to be connected to an absorption heat pump unit; a flue gas waste heat recovery device is used to recover flue gas and use the flue gas as a driving source to generate water at a second temperature, which is then connected to the absorption heat pump unit; the absorption heat pump unit uses exhaust steam as a driving heat source and water at the first and second temperatures as low-grade heat sources to raise the temperature of the water at the first and second temperatures to generate water at a third temperature, which is then output to the heating network; wherein, the third temperature is higher than the first and second temperatures.

[0016] To better understand the technical solution of this invention, the technical background involved in this invention will first be explained. In the field of centralized heating, heating design typically adopts a temperature system of 90°C supply water and 60°C return water, meaning that the heating network needs to obtain high-temperature hot water at 90°C to meet the heating needs of end users.

[0017] However, power plants continue to generate low-grade waste heat of approximately 42°C during the summer non-heating season. Due to the lack of efficient and stable energy storage methods, this waste heat is consistently released, resulting in significant energy waste. Meanwhile, while cross-seasonal geothermal energy storage and recycling technology has advantages such as large storage capacity and high stability, after heat extraction through ground source heat pump units, it can only produce hot water at a maximum temperature of approximately 45°C to 60°C. This leaves a significant temperature gap compared to the 90°C heating demand. If a multi-stage electrically driven heat pump is used in series to forcibly raise the temperature, the overall system coefficient of performance (COP) will decrease significantly, making it difficult to guarantee both economic efficiency and energy conservation.

[0018] Furthermore, although biomass energy is a renewable and clean energy source, capable of generating high-temperature steam for power generation and energy supply by burning biomass fuels such as straw and wood chips, its load stability is poor when used as a heat source alone due to seasonal fluctuations in fuel supply. Based on these three practical difficulties, this invention proposes a multi-energy synergistic heating system that deeply couples cross-seasonal geothermal energy storage, power plant waste heat, biomass cogeneration, and absorption heat pumps. This system achieves cross-seasonal energy storage and cascaded utilization by storing power plant waste heat during the non-heating season to raise the ground temperature and using exhaust steam from biomass power generation to drive an absorption heat pump to raise the temperature of low-temperature hot water on the ground source side to 90°C during the heating season.

[0019] like Figure 1 As shown, Figure 1 This is a schematic diagram of a multi-energy coordinated heating system provided in this application embodiment, including a group of buried pipe wells 15, a biomass cogeneration unit, a ground source heat pump unit 11, a flue gas waste heat recovery device 12, an absorption heat pump unit, and an electric boiler 9. The biomass cogeneration unit includes a biomass boiler 7, a steam turbine generator set 8, and a steam distribution cylinder; the ground source heat pump unit 11 includes an evaporator 1, a compressor 4, a condenser 2, and a throttling device 3; the flue gas waste heat recovery device 12 includes a sensible heat recovery heat exchanger and a condensation recovery heat exchanger; the absorption heat pump unit includes a first absorption heat pump 13 and a second absorption heat pump 14. The above subsystems are interconnected through pipelines, circulating pumps, and control valves to form a coordinated whole. The system's operation is divided into two phases based on time: a heat storage period and a heating period. The operation process of each phase is described in detail below.

[0020] The heat storage period refers to the non-heating period from the end of each heating season to the start of the next heating season, which is approximately 5 months in this embodiment. During this period, the core task of the system is to transport the low-grade waste heat generated by the power plant to the underground rock and soil layers for heat storage, so that the ground temperature gradually rises from its natural state and stabilizes at the preset target temperature, thereby laying the foundation for efficient heat extraction during the heating season.

[0021] In practical implementation, the underground well group 15 is an underground heat exchange structure used for both the heat storage and heating periods. It consists of multiple boreholes and heat exchange pipes installed in the boreholes. In this embodiment, the underground well group 15 adopts a dense array layout with a well spacing of 6 meters × 6 meters. The reason for adopting this high-density layout is that when the spacing between adjacent boreholes is small, the heat released by each borehole into the rock and soil can be superimposed inside the stratum, forming a concentrated heat storage area with a continuously rising temperature—that is, the "thermal core" effect commonly referred to in the art. This effect can effectively reduce the heat diffusion loss to the periphery of the well group and improve the overall heat storage efficiency.

[0022] The depth of each borehole is designed to be 150 to 300 meters. This depth range is located in a stratum with relatively stable geothermal properties, which avoids interference from surface climate fluctuations in shallow geothermal temperature and ensures the stability and controllability of the thermal storage process. The heat exchange pipes installed in the boreholes are double U-shaped pipes made of high-density polyethylene (HDPE100). Compared with single U-shaped pipes, double U-shaped pipes have a larger heat exchange area and lower flow resistance, which is conducive to efficient heat exchange between the heat exchange medium and the geothermal layer. Regarding the geothermal properties, the comprehensive thermal conductivity of the geothermal mass in the target area should not be less than 2.0 W / (m·K). Before the project is implemented, the actual thermal conductivity of the geothermal mass needs to be determined through a field thermal response test (TRT). The principle of this test is to inject heat of known power into the borehole, monitor the changes in the inlet and outlet water temperatures, and calculate key parameters such as the thermal conductivity of the geothermal mass and the borehole thermal resistance, providing basic input data for subsequent thermal storage control algorithms.

[0023] The operation process during the thermal storage period is as follows: The external waste heat source—namely, the waste heat 10 from the power plant—is transported via the power plant's existing heating network and the waste heat circulation pump 17 to the thermal storage inlet of the buried pipe well group 15 at approximately 42°C. After entering the buried pipe well group 15, the waste heat water flows downward along the heat exchange channel formed by the double U-shaped pipes. During the flow, it exchanges heat with the surrounding soil and rock layers through the pipe walls, gradually transferring heat into the soil and rock layers, causing the soil and rock layer temperature to rise continuously. The return water, which has cooled down after heat exchange, returns to the waste heat side of the power plant via the return water pipeline of the buried pipe well group 15, completing one thermal storage cycle. During the continuous thermal storage process of 5 months, the soil and rock layer temperature gradually increases from the initial natural ground temperature (usually about 12°C to 15°C) and eventually stabilizes at about 35°C, thus forming a thermal storage soil and rock layer. It should be noted that 35℃ is a target temperature that takes into account thermal storage efficiency, heat extraction demand, and ground safety. If the temperature is too low, the temperature difference on the evaporator side of the ground source heat pump will be insufficient during the heating season, resulting in a decrease in heat extraction efficiency. If the temperature is too high, it may cause changes in the mechanical properties of the soil and rock, while also increasing the loss of heat to the outside.

[0024] Regarding the selection of the heat exchange medium during the thermal storage period, in this embodiment, the first heat exchange medium injected into the buried well group 15 during the thermal storage period is clean water. The reason for choosing clean water instead of antifreeze during the thermal storage period is that clean water has a large specific heat capacity (approximately 4.2 kJ / (kg·℃)) and low viscosity, enabling it to achieve high heat exchange efficiency with low pumping power consumption under 42℃ waste heat conditions. Simultaneously, the operating temperature during the thermal storage period remains above 0℃, eliminating the risk of freezing and thus eliminating the need for antifreeze. This medium selection strategy significantly reduces system energy consumption and operating costs during the thermal storage period.

[0025] To achieve precise control of the thermal storage process, the system includes a temperature monitoring subsystem and a central controller. The temperature monitoring subsystem comprises multiple temperature monitoring wells installed within the buried well group 15. These wells are located in the central area, edge area, and reference area outside the well group. Within each monitoring well, a high-precision temperature sensor (using a PT1000 platinum resistance sensor with a measurement accuracy of ±0.1℃) is installed every 20 meters along the depth direction to collect formation temperature data at different depths in real time. After receiving data from all temperature sensors, the central controller calculates the average formation temperature Tavg within the well group and dynamically adjusts the operating frequency of the thermal storage circulation pump 16 based on the deviation between Tavg and the target temperature of 35℃, thereby controlling the circulation flow rate of the heat exchange medium.

[0026] The specific control strategy is implemented in three stages: When thermal storage begins, if the average formation temperature Tavg is below 25℃, it indicates a large temperature difference between the formation and the waste hot water. At this time, the thermal storage circulation pump 16 operates at full frequency and full load, rapidly injecting heat into the formation at a high flow rate to fully utilize the temperature difference advantage and improve the thermal storage rate. When the average formation temperature Tavg rises to the range of 30℃ to 35℃, the temperature difference gradually decreases, and the system enters a variable operating condition mode. The central controller reduces the operating frequency of the thermal storage circulation pump 16 and decreases the circulation flow rate through the variable frequency drive (VFD). The purpose of this is... By extending the residence time of the heat exchange medium in the buried pipe, the heat exchange between the medium and the soil layer is made more thorough, ensuring that the heat quality of the 42℃ waste heat is absorbed by the soil layer as much as possible, and avoiding the decrease in heat storage efficiency caused by excessively high return water temperature under high flow conditions. When the average formation temperature Tavg reaches 35℃, the system switches to a periodic micro-flow circulation isothermal maintenance mode, maintaining the temperature uniformity within the well group with only a very low flow rate. If the average formation temperature Tavg is detected to exceed 37℃, the central controller will automatically shut off the waste heat inlet valve and stop the heat storage circulation to prevent the formation from overheating. Through the above three-stage feedback control strategy, the system can accurately and stably maintain the formation temperature at around 35℃ during the 5-month heat storage period, creating favorable conditions for efficient heat extraction during the heating season.

[0027] The heating season refers to the annual centralized heating period, which in this embodiment is 150 days, operating continuously 24 hours a day. Before the start of the heating season, the system needs to first complete the heat exchange medium replacement operation: the clean water used during the heat storage period is discharged from the heat exchange channels of the buried pipe well group 15, and then refilled with brine antifreeze as the second heat exchange medium. The reason for this replacement operation is that during the heating season, the evaporator 1 side of the ground source heat pump unit 11 needs to operate under low-temperature conditions. The minimum supply and return water temperature of evaporator 1 is designed to be -2℃ / -7℃. If clean water is still used as the heat exchange medium, the clean water will freeze in this temperature range, which will not only prevent normal circulation but may also freeze and crack the pipeline, causing system damage. The freezing point of brine antifreeze is much lower than -7℃, which can maintain liquid flow under extreme low-temperature conditions, ensuring the safe and stable operation of the system. The discharged clean water and the collected brine antifreeze are collected through the drain valve into the corresponding dedicated storage tanks and sealed for storage. They will be replaced and used again when the next season changes, realizing the recycling of the medium. During media replacement, the system monitors the discharge and filling process through a liquid level sensor installed on the storage tank to ensure that clean water is completely discharged before injecting brine antifreeze, thus avoiding the mixing of the two media, which would dilute the brine concentration and reduce the antifreeze performance.

[0028] During the heating season, the coordinated operation of the various subsystems in the system is as follows: The biomass cogeneration unit operates continuously throughout the heating season and is the core supply hub for the system's heat and electricity. Biomass boiler 7 burns biomass fuels such as straw and sawdust to produce high-temperature, high-pressure steam at a pressure of 2.5 MPa and a temperature of 350°C, while also generating high-temperature flue gas. The high-temperature, high-pressure steam is transported to turbine generator set 8, which drives the turbine to rotate and generate electricity. Turbine generator set 8 adopts a self-consumption operation mode, meaning that the generated electricity is prioritized for use within the system itself and is not sent to the power grid. After the steam expands by doing work in turbine generator set 8, it discharges exhaust steam at a pressure of 0.6 MPa and a temperature of 200°C. It should be noted that the exhaust steam parameter of 0.6 MPa / 200℃ was chosen because it precisely meets the driving requirements of absorption heat pump units. Absorption heat pumps require medium-to-low pressure steam as the driving heat source to complete the absorption-desorption cycle. Excessively high steam parameters would increase the back pressure of the turbine, thus reducing power generation efficiency, while excessively low steam parameters would be insufficient to drive the absorption heat pump to achieve the required temperature rise. Therefore, 0.6 MPa / 200℃ is the optimal parameter that strikes a balance between power generation efficiency and heating demand.

[0029] The exhaust steam generated by the steam turbine generator set 8 is transported to the steam distribution cylinder via pipeline. The steam distribution cylinder is a pressure vessel whose function is to receive all the exhaust steam discharged from the steam turbine generator set 8 and then evenly distribute the exhaust steam to multiple branch outputs. In this embodiment, the outlet of the steam distribution cylinder is provided with two branches: branch A leads to the first absorption heat pump 13, which is used to drive the first absorption heat pump 13 to heat the low-temperature hot water from the ground source heat pump unit 11; branch B leads to the second absorption heat pump 14, which is used to drive the second absorption heat pump 14 to heat the low-temperature hot water from the flue gas waste heat recovery device 12. Each branch is equipped with an electric proportional integral regulating valve, and in conjunction with a pressure transmitter and a flow meter, the central controller distributes the exhaust steam flow by adjusting the opening of the electric proportional integral regulating valve according to the real-time heat load requirements of the two absorption heat pumps. For example, during periods of severe cold, when the load demand of the first absorption heat pump 13 is greater, the opening of the regulating valve in branch A increases to distribute more exhaust steam, while the opening of the regulating valve in branch B decreases accordingly. Conversely, when the amount of low-temperature hot water produced by the flue gas waste heat recovery device 12 increases, the distribution ratio in branch B increases. Through this dynamic adjustment method, the heat energy of the exhaust steam can be distributed between the two absorption heat pumps on demand, avoiding the problem of insufficient or excessive driving heat source on one side due to uneven distribution.

[0030] The electricity generated by the steam turbine generator set 8 is divided into two parts. One part of the electricity is used as the pre-set power supply and is sent to the ground source heat pump unit 11 and various circulating pumps (including the ground source heat pump evaporator circulating pump 19, the ground source heat pump condenser circulating pump 20, etc.) to provide the power required for the operation of the compressor 4 of the ground source heat pump unit 11 and various circulating pumps. When the biomass fuel supply is sufficient and the steam turbine generator set 8 is running at full load, the generated electricity may exceed the power consumption required by the ground source heat pump unit 11 and the circulating pump system. At this time, the remaining electricity is sent to the electric boiler 9. The electric boiler 9 uses the high-voltage electrode heating principle to heat water to a fourth temperature above 90°C, and after producing high-temperature hot water, it is output to the heating network through the electric boiler heating circulating pump 18 as a supplementary heat source for centralized heating. The significance of this design lies in converting "excess electricity" in the system into "heat that can be used for heating," thus avoiding electricity waste. It also provides a flexible peak-shaving mechanism—when there is a sudden surge in instantaneous heat load or a brief failure in other subsystems, the electric boiler 9 can quickly start to supplement heat, serving as an emergency backup. Furthermore, when fluctuations in biomass fuel supply lead to insufficient output from the turbine generator set 8, the system can also connect to municipal power as a supplementary power source, ensuring that critical equipment such as the ground source heat pump unit 11 does not shut down due to power outages.

[0031] Meanwhile, the high-temperature flue gas generated by the biomass boiler 7 is transported to the flue gas waste heat recovery device 12 for waste heat recovery. The flue gas waste heat recovery device 12 includes a sensible heat recovery heat exchanger and a condensation recovery heat exchanger connected in series. The high-temperature flue gas first enters the sensible heat recovery heat exchanger, where it exchanges heat with circulating water. The sensible heat in the flue gas—that is, the heat released due to the decrease in flue gas temperature—is transferred to the circulating water, raising the temperature of the circulating water to form preheated water. At the same time, the flue gas itself decreases in temperature to become cooled flue gas. The cooled flue gas then enters the condensation recovery heat exchanger, where the water vapor in the cooled flue gas undergoes a condensation phase change under conditions below the dew point temperature, releasing latent heat of vaporization—this latent heat is a relatively low-grade but considerable amount of heat in the waste heat of the flue gas, which would be lost with the flue gas emission if not recovered. The condensation recovery heat exchanger uses this latent heat to further heat the preheated water output from the sensible heat recovery heat exchanger, ultimately generating water at a second temperature. In this embodiment, the second temperature is approximately 40°C to 45°C. Water at this second temperature is transported to the second absorption heat pump 14 via the flue gas waste heat recovery circulation pump 22, serving as the low-grade heat source for the second absorption heat pump 14. Through a two-stage series connection of sensible heat recovery and latent heat recovery, the flue gas waste heat recovery device 12 can recover the available heat in the flue gas to the maximum extent, reducing the flue gas emission temperature to near ambient temperature, and significantly improving the overall thermal efficiency of the biomass boiler 7.

[0032] The operation of the ground source heat pump unit 11 during the heating season is as follows: The ground source heat pump evaporator circulation pump 19 drives the brine antifreeze to circulate between the buried pipe well group 15 and the evaporator 1. When the brine antifreeze flows through the buried pipe well group 15, it extracts heat from the heat storage soil layer. Since the ground temperature has been raised to about 35°C during the heat storage period, compared with the natural ground temperature without heat storage (about 12°C to 15°C), the heat storage soil layer can provide a higher heat source temperature, making the inlet water temperature on the evaporator 1 side significantly higher than that under normal operating conditions. This is the core value of the "cross-seasonal heat storage" of this invention: by increasing the heat source temperature on the evaporator side, the compression ratio required by the compressor 4 is reduced, thereby significantly improving the coefficient of performance (COP) of the ground source heat pump unit 11. After the brine antifreeze carrying heat enters the evaporator 1, it exchanges heat with the refrigerant in the evaporator 1. After absorbing heat, the refrigerant evaporates from a liquid state into a gaseous refrigerant at the first atmosphere pressure. The operating supply and return water temperature of evaporator 1 is designed to be -2℃ / -7℃. That is, the brine antifreeze enters evaporator 1 at a temperature of -2℃, releases heat and flows out at a temperature of -7℃, and then returns to the underground pipe well group 15 to continue to absorb heat from the heat storage rock and soil layer, forming a continuous heat extraction cycle.

[0033] The first-pressure gaseous refrigerant enters the compressor 4 from the refrigerant outlet of the evaporator 1. The compressor 4, driven by a pre-set portion of electricity supplied by the biomass cogeneration unit, compresses the first-pressure gaseous refrigerant, increasing its pressure to the second pressure and temperature, forming a high-temperature, high-pressure second-pressure gaseous refrigerant. This second-pressure gaseous refrigerant then enters the condenser 2, where it exchanges heat with the circulating heating and return water driven by the ground-source heat pump condenser circulation pump 20. After releasing heat in the condenser 2, the second-pressure gaseous refrigerant gradually condenses into a high-pressure liquid refrigerant. The released heat is transferred to the circulating water, raising its temperature to approximately 45°C. The operating supply and return water temperatures of the condenser 2 are designed to be 45°C / 40°C, meaning the circulating water enters the condenser 2 at 40°C and exits at 45°C after absorbing heat. It should be noted that the initial temperature of 45°C is still significantly lower than the 90°C supply water temperature required for centralized heating. If a traditional method were used to further raise the temperature through a series of multi-stage electrically driven heat pumps, it would not only consume a large amount of electricity, but also further reduce the COP of each heat pump stage as the compression ratio increases, resulting in extremely poor overall system efficiency. Therefore, this invention selects to deliver water at the initial temperature of 45°C to the first absorption heat pump 13, utilizing a steam-driven absorption heat pump for heating, thus achieving a cascaded connection between the electrically driven heat pump and the steam-driven heat pump.

[0034] The high-pressure liquid refrigerant flowing from condenser 2 enters throttling device 3. Throttling device 3 throttles and reduces the pressure of the high-pressure liquid refrigerant, lowering it to a third pressure below the first atmospheric pressure. During throttling, the refrigerant partially flashes, forming a low-temperature, low-pressure gas-liquid mixture. This mixture then enters evaporator 1 to continue absorbing heat from the underground well group 15 and evaporating, thus completing a full circulation loop of the refrigerant between evaporator 1, compressor 4, condenser 2, and throttling device 3. In this cycle, the second atmospheric pressure is higher than the first atmospheric pressure, and the first atmospheric pressure is higher than the third atmospheric pressure. This three-level pressure gradient ensures that the refrigerant can continuously undergo a thermodynamic cycle of "low-temperature heat absorption—compression and pressure increase—high-temperature heat release—throttling and pressure reduction" within the circulation loop.

[0035] The absorption heat pump unit is a key component in achieving the final heating temperature increase. The first absorption heat pump 13 receives water at a first temperature of 45°C from the condenser 2 of the ground source heat pump unit 11 as a low-temperature heat source, and simultaneously receives exhaust steam at 0.6MPa / 200°C from branch A of the steam distribution cylinder as a driving heat source. Inside the first absorption heat pump 13, the high-grade heat energy of the exhaust steam drives a lithium bromide-water solution to undergo a generation-absorption cycle. Through processes such as heating the dilute lithium bromide solution with exhaust steam in generator 5 to cause water evaporation and separation, and the concentrated solution in absorber 6 absorbing water vapor from the evaporator and releasing heat, the heat in the 45°C low-temperature hot water is raised to a higher temperature level, ultimately producing water at a third temperature of 90°C. Meanwhile, the second absorption heat pump 14 receives water at a second temperature (approximately 40°C to 45°C) output from the flue gas waste heat recovery device 12 as a low-temperature heat source, and receives exhaust steam from the steam distribution cylinder branch B as a driving heat source. It also heats the low-temperature hot water to a third temperature of 90°C through an absorption thermal cycle. The outlets of the first absorption heat pump 13 and the second absorption heat pump 14 are connected to the heating network, and the water at the third temperature of 90°C is output to the centralized heating network via the absorption heat pump heating circulation pump 21 to meet the heating needs of end users.

[0036] This cascaded utilization method, which combines ground-source heat pumps to produce medium-temperature water with absorption heat pumps to heat the water to high temperatures using steam, offers significant advantages over purely electric multi-stage heat pump series solutions. The ground-source heat pump only needs to raise the temperature from the ground's thermal storage temperature to 45°C, resulting in a low compression ratio and high COP. The task of raising the temperature from 45°C to 90°C is handled by the absorption heat pump, which uses exhaust steam as its driving source. The absorption heat pump consumes the steam heat energy generated from biomass combustion, rather than electricity, thus avoiding the problem of a sharp drop in efficiency for electrically driven heat pumps under high-temperature conditions. By combining the strengths of both types of heat pumps in a cascaded manner, the overall energy utilization efficiency of the system is significantly improved.

[0037] During the 150-day heating season, the outdoor ambient temperature follows a pattern of "mild at the beginning, severe cold in the middle, and warming at the end" with seasonal changes, and the corresponding building heat load demand also fluctuates. In order to enable the system to adapt efficiently to different load conditions, the central controller implements a graded operation control strategy based on multi-dimensional information such as outdoor temperature, ground temperature, biomass fuel supply status, and operating parameters of each device.

[0038] During the initial and final stages of the heating season, outdoor temperatures are relatively high, and the building's heat load demand is low. At this time, the system operates in low-load mode. The biomass boiler 7 operates at medium to low load, and the electricity generated by the turbine generator set 8 drives the ground-source heat pump unit 11 to produce water at a first temperature of 45°C. This hot water enters the first absorption heat pump 13. Since the heat load is low at this time, the required supply water temperature can be reduced to approximately 80°C to meet heating needs. Therefore, only a small amount of exhaust steam needs to be allocated to the first absorption heat pump 13 to complete the heating task. In this mode, the second absorption heat pump 14 can be flexibly started and stopped depending on the heat generation of the flue gas waste heat recovery device 12. The entire system operates at a low output level, avoiding unnecessary energy consumption.

[0039] During periods of severe cold, outdoor temperatures drop to extremely low levels, building heat loads reach peak values, and the heating network requires the water supply temperature to reach 90℃. At this time, the system switches to high-load mode: biomass boiler 7 operates at full load, steam turbine generator set 8 generates electricity at full load and produces the maximum amount of exhaust steam; ground source heat pump unit 11 continuously operates to produce water at a first temperature of 45℃; the first absorption heat pump 13 and the second absorption heat pump 14 operate at full load simultaneously, and the steam distributor allocates the exhaust steam to the two absorption heat pumps as needed, making full use of the exhaust steam heat energy and flue gas waste heat to raise the water supply temperature to 90℃, maximizing the output of heat to meet the peak load demand during severe cold periods.

[0040] When power output exceeds the system's own power consumption—for example, when the heating load is low but the biomass boiler 7 still needs to maintain a certain output to ensure steam supply—a power surplus will occur in the system. At this time, the central controller automatically triggers the startup logic of the electric boiler 9, transferring all the surplus power generated by the turbine generator set 8 to the electric boiler 9. The electric boiler 9 then uses high-voltage electrode heating to produce high-temperature hot water above 90°C and stores it as peak-shaving support or emergency backup for the system. This "electricity-to-heat" design ensures that all energy generated by biomass combustion—whether in the form of steam, electricity, or waste heat from flue gas—can be efficiently utilized regardless of the system's load condition, preventing energy waste due to mismatches between power or heat supply and demand.

[0041] In terms of system operation safety, the central controller is also equipped with a temperature safety interlock mechanism. When the temperature of the inlet water of the buried pipe detected by the circulating pump 19 of the ground source heat pump evaporator is lower than -7℃, it indicates that the available heat of the heat storage soil layer is almost exhausted or the local temperature of the stratum is too low. Continued operation may cause the brine antifreeze to approach the freezing point and endanger the system safety. At this time, the system automatically reduces the output of the ground source heat pump unit 11 or shuts it down for protection. When the steam pressure of the biomass boiler 7 is abnormal—for example, due to the interruption of fuel supply causing a sudden drop in steam pressure—the output of the turbine generator unit 8 will not be able to be maintained. At this time, the system automatically switches to the emergency safety mode, and the electric boiler 9 connects to the municipal power for emergency heating and supplements the heat through the existing heating network of the power plant to ensure uninterrupted heating.

[0042] In summary, this invention deeply couples and coordinates four technologies—cross-seasonal geothermal energy storage, power plant waste heat, biomass cogeneration, and absorption heat pumps—to construct a complete multi-energy coordinated heating system encompassing "summer heat storage—winter heat extraction—tiered heating." During the non-heating season, the system utilizes power plant waste heat to store heat in the geothermal layer, transforming previously wasted low-grade waste heat into stable underground heat storage resources. During the heating season, the system uses biomass power generation to drive a ground source heat pump to extract medium-temperature hot water from the stored geothermal layer. The exhaust steam from the biomass power generation then drives an absorption heat pump to raise the temperature of this medium-temperature hot water to 90°C, meeting the requirements for centralized heating. Simultaneously, the system deeply recovers and utilizes the waste heat from the biomass boiler's flue gas, and uses an electric boiler as a peak-shaving and emergency measure. The entire system realizes cross-seasonal storage and utilization of waste heat from power plants, cascade utilization of biomass energy through cogeneration, efficient extraction of geothermal energy, and deep recovery of various types of waste heat. It effectively solves the problems of seasonal waste, insufficient outlet water temperature, and load fluctuation that exist when the three energy sources operate independently in existing technologies. It fills the heat source gap in regional centralized heating, significantly reduces fossil energy consumption, and provides a practical and feasible technical path for achieving clean heating and "dual carbon" goals.

[0043] Figure 2 This is a schematic flowchart of a multi-energy coordinated heating method provided in an embodiment of this application; as shown... Figure 2 As shown, the method includes S101-S104: S101, during the non-heating season, transfers the waste heat generated by the external waste heat source to the soil and rock layer for heat storage, thus generating a heat-storing soil and rock layer.

[0044] During the non-heating season, waste heat from external heat sources is transferred to the soil and rock layers for heat storage, creating a heat-storing soil and rock layer. This step is performed during the non-heating season because external waste heat sources—such as the approximately 42°C low-grade waste heat continuously generated by power plants during daily operation—cannot be absorbed and utilized by the heating network during the non-heating season. If not collected and stored, it would be directly released into the environment, resulting in energy waste. Soil and rock layers have natural advantages such as large heat capacity, good insulation performance, and long storage periods. Transferring this waste heat to underground soil and rock layers for cross-seasonal storage during the non-heating season can transform previously useless low-grade heat energy into a medium-temperature heat source that can be extracted and utilized during the heating season. In practice, a heat exchange medium is continuously circulated between the external waste heat source and the underground well group by a heat storage circulation pump. After absorbing 42°C of waste heat from the external waste heat source, the heat exchange medium flows into the underground well group. As it flows downward along the double U-shaped heat exchange pipes in the underground well group, it exchanges heat with the surrounding soil and rock layers through the pipe walls, gradually releasing the heat it carries into the soil and rock layers, causing the soil and rock layer temperature to continuously rise from the initial natural ground temperature (usually about 12°C to 15°C). During the approximately five-month continuous heat storage process throughout the non-heating season, the system monitors the average ground temperature in real time using temperature sensors deployed in a network of buried wells. The central controller dynamically adjusts the operating frequency of the heat storage circulation pump and the circulation flow rate of the heat exchange medium based on the monitoring data: in the initial stage of heat storage, when the ground temperature is low and the temperature difference is large, a high flow rate is used for rapid heat injection; in the middle and later stages of heat storage, as the ground temperature gradually rises and the temperature difference decreases, the flow rate is reduced to prolong the residence time of the heat exchange medium in the pipes, thereby improving heat exchange efficiency; when the average ground temperature reaches approximately 35°C, a low-flow maintenance mode is switched to prevent overheating. Through this continuous and controlled heat storage process, the temperature of the soil layer eventually stabilizes at approximately 35°C, thus generating a heat storage soil layer. Compared to the untreated natural soil layer, this heat storage soil layer has a temperature increase of approximately 20°C to 23°C. This temperature increase lays a crucial foundation for efficient heat extraction from underground during the heating season, enabling the evaporator side of the ground source heat pump unit to obtain a higher inlet water temperature in subsequent steps, thereby reducing the compressor's compression ratio and significantly improving the system's coefficient of performance (COP).

[0045] S102 extracts heat from the heat-storing rock and soil layer during the heating season and generates water at the first temperature based on the heat.

[0046] During the heating season, heat is extracted from the thermal storage rock and soil layer, and water at a first temperature is generated based on this heat. The purpose of this step is to extract the heat energy stored in the thermal storage rock and soil layer across seasons in step S101, and to improve its quality to a medium temperature level suitable for subsequent heating stages through the thermal cycle of the ground source heat pump unit. Before the start of the heating season, the clean water heat exchange medium used during the heat storage period in the buried pipe well group needs to be drained and replaced with brine antifreeze as the heat exchange medium for the heating season. This is because the operating temperature on the evaporator side of the ground source heat pump unit is as low as -7°C during the heating season. Clean water would freeze and crack the pipes at this temperature, while the freezing point of brine antifreeze is much lower than -7°C, ensuring safe flow under low-temperature conditions. In practice, the evaporator circulation pump of the ground source heat pump drives the brine antifreeze to continuously circulate between the evaporator of the buried pipe well group and the ground source heat pump unit. As the brine antifreeze flows through the buried pipe well group, it absorbs heat from the approximately 35°C heat storage soil layer before entering the evaporator. In the evaporator, it exchanges heat with the refrigerant inside the pipes, transferring the heat it carries to the refrigerant, causing it to evaporate into a gaseous state. After its own temperature decreases, the brine antifreeze returns to the buried pipe well group to continue extracting heat. The supply and return water temperatures of the evaporator are designed to be -2°C / -7°C. The gaseous refrigerant, after absorbing heat and evaporating in the evaporator, then enters the compressor. The compressor, driven by electricity, compresses the gaseous refrigerant, increasing its temperature and pressure simultaneously. The high-temperature, high-pressure gaseous refrigerant then enters the condenser, where it releases heat to the circulating water and condenses into a liquid state. The circulating water absorbs heat and its temperature rises, thus generating water at a first temperature, which in this embodiment is approximately 45°C. The supply and return water temperatures of the condenser are designed to be 45°C / 40°C. After condensation in the condenser, the liquid refrigerant is depressurized and cooled by a throttling device before re-entering the evaporator, completing the closed-loop thermodynamic cycle of the refrigerant. The effect of this step is that, since the temperature of the heat storage soil layer has been pre-raised to approximately 35°C in step S101, far exceeding the 12°C to 15°C of the natural soil layer, the evaporator side obtains a higher-grade low-grade heat source. The compressor only needs a lower compression ratio to raise the refrigerant to the required temperature and pressure level on the condenser side. Therefore, the ground source heat pump unit operates at a higher energy efficiency coefficient, efficiently generating water at a first temperature of 45°C with less electricity consumption. However, it should be noted that the first temperature of 45°C is still significantly lower than the 90°C supply water temperature typically required by centralized heating networks. If the temperature is further increased by forcibly connecting multiple electrically driven heat pumps in series, the energy efficiency coefficient will decrease significantly with each additional compression stage, making the overall system economics unacceptable. Therefore, the water at the first temperature needs to be transported to the subsequent step S104 for further heating by another type of heat pump.

[0047] S103 burns biomass fuel to generate flue gas, which is then used as a driving source to generate water at a second temperature.

[0048] The process involves burning biomass fuel to generate flue gas, which is then used as a driving source to produce water at a second temperature. The purpose of this step is to fully utilize the waste heat from the flue gas generated during biomass combustion, recovering the sensible and latent heat that would otherwise be lost during emissions and converting it into usable medium-temperature hot water, serving as another low-temperature heat source for subsequent heating stages. The reason for this waste heat recovery is that biomass boilers inevitably emit a large amount of high-temperature flue gas while burning biomass fuels such as straw and sawdust to produce high-temperature, high-pressure steam. This flue gas typically carries 10% to 15% of the total calorific value of the fuel; direct emission would not only waste energy but also increase thermal pollution from the water vapor in the flue gas. In practice, a biomass boiler burns biomass fuel to produce high-temperature flue gas. This high-temperature flue gas first enters the sensible heat recovery heat exchanger in the flue gas waste heat recovery device. In the sensible heat recovery heat exchanger, the high-temperature flue gas undergoes convective heat exchange with circulating water, causing the flue gas temperature to decrease and releasing sensible heat (sensible heat refers to the portion of heat released by the flue gas due to temperature reduction, during which the flue gas does not undergo a phase change). The circulating water absorbs the sensible heat and its temperature rises to form preheated water, while the flue gas itself cools down to become cooled flue gas. The cooled flue gas then enters the condensation recovery heat exchanger, where the temperature of the cooled flue gas is further reduced to below the dew point temperature. The water vapor in the flue gas undergoes a condensation phase change, changing from a gaseous state to a liquid state. During this process, the latent heat of vaporization is released (latent heat refers to the heat absorbed or released by a substance during a phase change, in this case, the portion of heat released when water vapor condenses into liquid water). The condensation recovery heat exchanger uses this latent heat to further heat the preheated water from the sensible heat recovery heat exchanger, ultimately generating water at a second temperature, which in this embodiment is approximately 40°C to 45°C. Through a deep heat recovery method that combines sensible heat recovery and latent heat recovery in a two-stage series, the emission temperature of the flue gas is significantly reduced to near ambient temperature, thus significantly improving the overall thermal efficiency of the biomass boiler. A considerable amount of heat that would otherwise be lost with the flue gas emission is converted into water at a second temperature, becoming an effective heat source for the system's heating. The water at this second temperature, like the water at the first temperature generated in step S102, is also below the 90°C required for centralized heating and needs further heating in subsequent steps.

[0049] It should be noted that the biomass fuel combustion process in step S103 generates not only flue gas but also high-temperature, high-pressure steam. This high-temperature, high-pressure steam is transported to a steam turbine generator set to drive power generation. On the one hand, it provides the necessary power for the compressor and circulating pumps of the ground source heat pump unit in step S102. On the other hand, the low- and medium-pressure exhaust steam discharged from the steam turbine generator set after it has done its work serves as the driving heat source for the absorption heat pump in step S104, realizing the cascade utilization of biomass combustion energy between power generation and heating. When the power generated by the steam turbine generator set exceeds the consumption of the ground source heat pump unit and the circulating pump system, the surplus power is transported to an electric boiler. The electric boiler heats the water to a fourth temperature above 90°C before outputting it to the heating network as a peak-shaving supplementary heat source, ensuring that all the energy from biomass combustion is utilized efficiently.

[0050] S104 uses water at a first temperature and water at a second temperature as a low-temperature heat source to raise the temperature of the water at the first temperature and water at the second temperature to generate water at a third temperature, and outputs the water at the third temperature to the heating network; wherein, the third temperature is higher than the first temperature and the second temperature.

[0051] Using water at a first temperature and water at a second temperature as low-grade heat sources, the water at the first and second temperatures is heated to generate water at a third temperature, which is then output to the heating network. This third temperature is higher than the first and second temperatures. This step is crucial for achieving the final heating target of the entire method. Its core objective is to address the problem that the water at approximately 45°C (first temperature) and approximately 40°C to 45°C (second temperature) produced in steps S102 and S103, respectively, cannot directly meet the 90°C supply temperature requirement of the centralized heating network. This is achieved by introducing an absorption heat pump driven by steam to achieve efficient heating with a large temperature difference. The reason for choosing an absorption heat pump instead of continuing to use an electrically driven compression heat pump to complete the temperature rise from 45°C to 90°C in this step is that the absorption heat pump uses steam thermal energy as its driving source instead of electricity. Its working principle is to use lithium bromide-water and other working fluids to carry out an absorption-desorption thermodynamic cycle between the generator and the absorber. By consuming high-grade steam thermal energy, it "transfers" the heat from the low-grade heat source to a high-temperature level. Compared with the inherent defects of electrically driven compression heat pumps, such as the sharp increase in compression ratio and the significant decrease in energy efficiency coefficient under large temperature difference conditions, the absorption heat pump can maintain a relatively stable operating efficiency within the temperature difference range from 45°C to 90°C. Moreover, the driving steam it consumes comes precisely from the exhaust steam of the turbine generator set in step S103. The pressure of this exhaust steam is about 0.6 MPa and the temperature is about 200°C, which is within the optimal driving parameter range of the absorption heat pump, thus realizing the full utilization of the exhaust steam thermal energy.

[0052] Please see Figure 3 This is a schematic diagram of the structure of an electronic device provided in an embodiment of this application. Figure 3As shown, the electronic device 1000 may include: at least one processor 1001, at least one network interface 1004, a user interface 1003, a memory 1005, and at least one communication bus 1002.

[0053] The communication bus 1002 is used to realize the connection and communication between these components.

[0054] The user interface 1003 may include a display screen and a camera. Optionally, the user interface 1003 may also include a standard wired interface and a wireless interface.

[0055] The network interface 1004 may optionally include a standard wired interface or a wireless interface (such as a Wi-Fi interface).

[0056] The processor 1001 may include one or more processing cores. The processor 1001 connects to various parts of the server using various interfaces and lines, and performs various server functions and processes data by running or executing instructions, programs, code sets, or instruction sets stored in the memory 1005, and by calling data stored in the memory 1005. Optionally, the processor 1001 may be implemented using at least one hardware form of Digital Signal Processing (DSP), Field-Programmable Gate Array (FPGA), or Programmable Logic Array (PLA). The processor 1001 may integrate one or a combination of several of the following: Central Processing Unit (CPU), Graphics Processing Unit (GPU), and modem. The CPU primarily handles the operating system, user interface, and applications; the GPU is responsible for rendering and drawing the content to be displayed on the screen; and the modem handles wireless communication. It is understood that the modem may also not be integrated into the processor 1001 and may be implemented as a separate chip.

[0057] The memory 1005 may include random access memory (RAM) or read-only memory. Optionally, the memory 1005 may include a non-transitory computer-readable storage medium. The memory 1005 can be used to store instructions, programs, code, code sets, or instruction sets. The memory 1005 may include a program storage area and a data storage area, wherein the program storage area may store instructions for implementing an operating system, instructions for at least one function (such as touch function, sound playback function, image playback function, etc.), instructions for implementing the above-described method embodiments, etc.; the data storage area may store data involved in the above-described method embodiments, etc. Optionally, the memory 1005 may also be at least one storage device located remotely from the aforementioned processor 1001. Figure 3 As shown, the memory 1005, which serves as a computer storage medium, may include an operating system, a network communication module, a user interface module, and an application program for a multi-energy coordinated heating method.

[0058] exist Figure 3 In the electronic device 1000 shown, the user interface 1003 is mainly used to provide an input interface for the user and to obtain the user input data; while the processor 1001 can be used to call an application program stored in the memory 1005 for a multi-energy coordinated heating method. When executed by one or more processors, the electronic device performs one or more of the methods described in the above embodiments.

[0059] An electronic device readable storage medium stores instructions that, when executed by one or more processors, cause the electronic device to perform one or more of the methods described in the above embodiments.

[0060] It should be noted that, for the sake of simplicity, the foregoing method embodiments are all described as a series of actions. However, those skilled in the art should understand that this application is not limited to the described order of actions, as some steps may be performed in other orders or simultaneously according to this application. Furthermore, those skilled in the art should also understand that the embodiments described in the specification are preferred embodiments, and the actions and modules involved are not necessarily essential to this application.

[0061] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0062] In the several embodiments provided in this application, it should be understood that the disclosed apparatus can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative; for instance, the division of units is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the displayed or discussed mutual couplings, direct couplings, or communication connections may be through some service interfaces; indirect couplings or communication connections between devices or units may be electrical or other forms.

[0063] The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of this embodiment according to actual needs.

[0064] Furthermore, the functional units in the various embodiments of this application can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit. The integrated unit can be implemented in hardware or as a software functional unit.

[0065] If the integrated unit is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage device (CMD). Based on this understanding, the technical solution of this application, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a memory and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of this application. The aforementioned memory includes various media capable of storing program code, such as USB flash drives, portable hard drives, magnetic disks, or optical disks.

[0066] The foregoing description is merely an exemplary embodiment of this disclosure and should not be construed as limiting the scope of this disclosure. Any equivalent changes and modifications made in accordance with the teachings of this disclosure shall still fall within the scope of this disclosure. Other embodiments of this disclosure will be readily apparent to those skilled in the art upon consideration of the specification and practice of the disclosure herein. This application is intended to cover any variations, uses, or adaptations of this disclosure that follow the general principles of this disclosure and include common knowledge or customary techniques in the art not described herein. The specification and embodiments are to be considered exemplary only, and the scope and spirit of this disclosure are defined by the claims.

Claims

1. A multi-energy source cooperative heating system, characterized in that, The system includes: a cluster of underground pipe wells, a biomass cogeneration unit, a ground source heat pump unit, a flue gas waste heat recovery device, and an absorption heat pump unit; wherein... The underground pipe well group is used to connect with the heating end of an external waste heat source during the non-heating season, and transfer the waste heat generated by the external waste heat source to the soil and rock layer for heat storage, thereby generating a heat storage soil and rock layer. The biomass cogeneration unit is used to burn biomass fuel to generate electricity, exhaust steam and flue gas, and transmits a preset portion of the electricity to the ground source heat pump unit and transmits the exhaust steam to the absorption heat pump unit. The ground source heat pump unit is used to extract heat from the heat storage rock and soil layer during the heating season using a preset portion of electricity as a driving source, generate water at a first temperature based on the heat, and connect the water at the first temperature to the absorption heat pump unit. The flue gas waste heat recovery device is used to recover flue gas, generate water at a second temperature using the flue gas as a driving source, and connect the water at the second temperature to the absorption heat pump unit. The absorption heat pump unit is used to use the exhaust steam as a driving heat source and the water at the first temperature and the water at the second temperature as low-temperature heat sources to heat the water at the first temperature and the water at the second temperature to generate water at the third temperature, and output the water at the third temperature to the heating network; wherein the third temperature is higher than the first temperature and the second temperature.

2. The multi-energy source coordinated heating system of claim 1, wherein, The buried well group includes: heat exchange channels for circulating heat exchange medium, a heat storage inlet, and a heat extraction outlet; wherein... The heat storage inlet is used to connect with the heating end of an external waste heat source during the non-heating season, and to transfer the waste heat generated by the external waste heat source to the soil and rock layer through the first heat exchange medium in the heat exchange channel for heat storage, thereby generating a heat storage soil and rock layer. The heat extraction outlet is used to connect with the ground source heat pump unit during the heating season, so as to transfer the heat stored in the heat storage rock and soil layer to the ground source heat pump unit through the second heat exchange medium in the heat exchange channel, so that the ground source heat pump unit can generate water at the first temperature according to the heat.

3. The multi-energy source coordinated heating system of claim 1, wherein, The ground source heat pump unit includes: an evaporator, a compressor, a condenser, and a throttling device; wherein, The evaporator is connected to the heat outlet of the buried well group and is used to receive the heat stored in the heat storage rock and soil layer. Through heat exchange between the heat exchange medium and the refrigerant, the heat is transferred to the refrigerant, causing the refrigerant to evaporate into a first-pressure gaseous refrigerant. The compressor is connected to the refrigerant outlet of the evaporator and is driven by the electricity of the preset part. It is used to compress the first pressure gaseous refrigerant into a second pressure gaseous refrigerant and deliver the second pressure gaseous refrigerant to the condenser. The condenser is connected to the refrigerant outlet of the compressor and is used to transfer the heat of the second-pressure gaseous refrigerant to the circulating water through heat exchange between the second-pressure gaseous refrigerant and the circulating water to generate water at the first temperature, and then connect the water at the first temperature to the absorption heat pump unit. The throttling device is connected between the refrigerant outlet of the condenser and the refrigerant inlet of the evaporator. It is used to throttle and reduce the pressure of the second-pressure gaseous refrigerant after heat exchange in the condenser to generate a third-pressure refrigerant, and then transport the third-pressure refrigerant back to the evaporator to form a refrigerant circulation loop. The second pressure is higher than the first pressure, and the first pressure is higher than the third pressure.

4. The multiple energy source coordinated heating system of claim 1, wherein, The biomass cogeneration unit includes: a biomass boiler, a steam turbine generator set, and a steam distribution cylinder; wherein... The biomass boiler is used to burn biomass fuel to generate steam and flue gas, and to deliver the steam to the steam turbine generator set and the flue gas to the flue gas waste heat recovery device. The steam turbine generator set is connected to the steam outlet of the biomass boiler and is used to drive the generator to produce electricity using the steam as power, and to produce exhaust steam. A preset portion of the electricity is transmitted to the ground source heat pump unit, and the exhaust steam is transmitted to the steam distribution cylinder. The steam distribution cylinder is connected to the exhaust port of the steam turbine generator set to receive exhaust steam and transport it to the absorption heat pump unit as the driving heat source for the absorption heat pump unit.

5. The multiple energy source coordinated heating system of claim 1, wherein, The flue gas waste heat recovery device includes: a sensible heat recovery heat exchanger and a condensation recovery heat exchanger; wherein... The sensible heat recovery heat exchanger is connected to the flue gas emission end of the biomass cogeneration unit and is used to receive the flue gas generated by the biomass cogeneration unit. Through heat exchange between the flue gas and circulating water, the sensible heat in the flue gas is recovered to generate preheated water and cooled flue gas, and the cooled flue gas is transported to the condensation recovery heat exchanger. The condensation recovery heat exchanger is connected to the flue gas outlet of the sensible heat recovery heat exchanger and is used to receive the cooled flue gas. By condensing and exchanging heat with the cooled flue gas, the latent heat of vaporization of water vapor in the cooled flue gas is recovered, the preheated water is heated to generate water at a second temperature, and the water at the second temperature is connected to the absorption heat pump unit.

6. The multiple energy source coordinated heating system of claim 1, wherein, The absorption heat pump unit includes: a first absorption heat pump and a second absorption heat pump; wherein... The first absorption heat pump is connected to the exhaust steam output end of the biomass cogeneration unit and the water outlet end of the ground source heat pump unit, and is used to use part of the exhaust steam as a driving heat source and water at the first temperature as a low-grade heat source to heat the water at the first temperature to generate water at the third temperature. The second absorption heat pump is connected to the exhaust steam output end of the biomass cogeneration unit and the water outlet end of the flue gas waste heat recovery device, and is used to heat the water at the second temperature by using part of the exhaust steam as a driving heat source and the water at the second temperature as a low-grade heat source to generate the water at the third temperature. The outlet of the first absorption heat pump and the outlet of the second absorption heat pump are connected to the heating network to output water at a third temperature to the heating network.

7. The multiple energy source coordinated heating system of claim 1, wherein, The system also includes: an electric boiler; wherein... The electric boiler is connected to the power output terminal of the biomass cogeneration unit, and is used to use the power other than the preset part of the power as a driving source to produce water at a fourth temperature, and output the water at the fourth temperature to the heating network as a supplementary heat source for the heating network; wherein, the fourth temperature is higher than the first temperature and the second temperature.

8. A method of multi-energy source cooperative heating, characterized in that, The method includes: During the non-heating season, the waste heat generated by external waste heat sources is transferred to the soil and rock layers for heat storage, thus creating a heat-storing soil and rock layer. During the heating season, heat is extracted from the heat-storing rock and soil layer, and water at a first temperature is generated based on the heat. Burning biomass fuel produces flue gas, which is then used as a driving source to generate water at a second temperature. Using water at the first temperature and water at the second temperature as low-temperature heat sources, the water at the first temperature and water at the second temperature are heated to generate water at the third temperature, and the water at the third temperature is output to the heating network; wherein, the third temperature is higher than the first temperature and the second temperature.

9. An electronic device, comprising: The device includes a processor, a memory, a user interface, and a network interface. The memory is used to store instructions, the user interface and the network interface are used to communicate with other devices, and the processor is used to execute the instructions stored in the memory to cause the electronic device to perform the method as described in any one of claims 8.

10. A computer-readable storage medium, characterized in that, The computer program is stored that can be loaded by a processor and executed as described in any one of claims 8.

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