Boiler peak regulation and heat supply system and operating method therefor

Abstract

Provided are a boiler peak regulation and heat supply system and an operating method therefor. The boiler peak regulation and heat supply system comprises a heat pump assembly, a power generation assembly (3) and a boiler assembly; the heat pump assembly comprises a mechanical heat pump unit (1) and an absorption heat pump unit (2), at least one absorption heat pump unit (2) is provided, and the mechanical heat pump unit (1) is connected to the output end of the power generation assembly (3) by means of a clutch mechanism (4); the boiler assembly comprises a boiler unit (5) and a steam turbine unit (6) which are circulatively connected, the steam turbine unit (6) is connected to the power generation assembly (3) and the absorption heat pump unit (2), and heat generated by the boiler unit (5) during operation is separately transferred to the power generation assembly (3) and the absorption heat pump unit (2) by means of the steam turbine unit (6); when the clutch mechanism (4) is in a connected state, the power generation assembly (3) enables variable load by means of the mechanical heat pump unit (1).

Description

A boiler peak-shaving heating system and its operation method CROSS-REFERENCE TO RELATED APPLICATIONS This application claims priority to the Chinese patent application filed with the China Patent Office on February 26, 2024, with application number 202410209451X and invention name “A boiler peak-shaving heating system and its operation method”, the entire contents of which are incorporated herein by reference. Technical Field The present application relates to the field of deep peak regulation and heat supply coordination technology, in particular to a boiler peak regulation heating system and its operation method. Background Art To build a clean, low-carbon, safe, and efficient energy system, control the total amount of fossil energy, focus on improving utilization efficiency, and implement renewable energy substitution, my country needs to deepen power system reform and build a new power system dominated by renewable energy. The unpredictable and discontinuous nature of renewable energy generation leads to unstable power, which affects grid power quality and prevents some renewable energy generation from entering the grid, resulting in "wind and solar curtailment." How to absorb this curtailed power is a pressing issue. To address the low penetration of renewable energy generation into the grid, peak-shaving by thermal power units, which account for a large proportion of generating capacity, has become an effective way to absorb renewable energy. Currently, the minimum operating load of coal-fired boilers in my country is 40-50% of rated load, which is still significantly lower than the world's advanced minimum technical output of 20-30% in countries like Germany and Denmark. Due to the unique characteristics of my country's energy resource structure, coal-fired power generation will continue to exist for a long time. Therefore, in order to provide more high-quality, flexible peak-shaving power, achieve synergistic power generation between traditional and renewable energy sources, and build a reliable and flexible power system, the participation of coal-fired power generation in peak-shaving is an inevitable choice. Boiler units sometimes need to provide heating in winter. The inherent coupling between heat and electricity output in thermal power units, especially back-pressure units, limits power generation under corresponding heat loads, resulting in poor peak-shaving performance. Heat pumps, as highly efficient and energy-efficient devices, can fully utilize low-quality thermal energy. Through a small amount of reverse cycle net work, they can generate a large amount of high-quality heat, effectively utilizing otherwise inaccessible low-quality heat. Based on the above characteristics, it is necessary to develop a technology that can combine heat pump technology and units to give full play to their peak-shaving and heating advantages, and achieve the effect of using heat pumps to produce heat under the same heat load, so as to reduce the power generation of electric field units and achieve deep peak regulation. Summary of the Invention The present application aims to solve one of the technical problems in the related art at least to a certain extent. To this end, the embodiments of the present application propose a boiler peak-shaving heating system and an operation method thereof, which can achieve a better peak-shaving effect while meeting the heating demand. According to the embodiment of the present application, the boiler peak-shaving heating system provided includes a heat pump component, a power generation component and a boiler component. The heat pump component includes a mechanical heat pump unit and an absorption heat pump unit. The number of the absorption heat pump unit is at least one. The mechanical heat pump unit is connected to the output end of the power generation component through a clutch mechanism. The boiler component includes a boiler unit and a turbine unit that are cyclically connected. The turbine unit is connected to the power generation component and the absorption heat pump unit. The heat generated by the boiler unit during operation is respectively transported to the power generation component and the absorption heat pump unit through the turbine unit; when the clutch mechanism is in a connected state, the power generation component realizes variable load through the mechanical heat pump unit. According to the boiler peak-shaving heating system of the embodiment of the present application, the clutch mechanism can be used to realize the deep operation of the boiler assembly. Flexible operation during peak-shaving: During the low-load operation of the power grid, the absorption heat pump unit produces heat of different qualities for residential and industrial use, realizing efficient cascade utilization of energy, having high economic benefits and being more environmentally friendly, helping to reduce energy waste, and realizing flexible adjustment of heating and power generation by changing the distribution of working fluids; when the power grid needs to change load quickly, the mechanical heat pump unit can be enabled to enable the mechanical heat pump heating system to generate a large amount of low-temperature heat for residential heating, alleviating the problem of tight heating and industrial heat use in winter, and at the same time quickly reducing the electrical load supplied to the power grid, realizing rapid and deep peak-shaving of the unit. In some embodiments, the steam turbine unit and the absorption heat pump unit are connected via a plurality of air extraction circuits, and any one of the air extraction circuits is provided with a central regulating valve with adjustable opening. In some embodiments, the exhaust circuit includes several exhaust branches and an exhaust main line. Any exhaust branch is provided with a check valve and an electric gate valve. All the exhaust branches are connected to the exhaust main line, and the exhaust main line is connected to the absorption heat pump unit. In some embodiments, the steam turbine unit includes a high-pressure cylinder, an intermediate-pressure cylinder, and a low-pressure cylinder connected in sequence, and each of the high-pressure cylinder, the intermediate-pressure cylinder, and the low-pressure cylinder includes a plurality of exhaust heating components; The air extraction heating assembly includes an air extraction stage group and a heater, and all the air extraction stage groups are arranged in sequence along the axial direction of the steam turbine group; A reheater is provided between the high-pressure cylinder and the medium-pressure cylinder, and two adjacent air extraction stage groups are connected via the reheater. In some embodiments, the intermediate pressure cylinder includes two exhaust gas heating assemblies, two adjacent exhaust gas heating assemblies are connected via an intermediate pressure reflux assembly, the intermediate pressure reflux assembly includes an intermediate pressure reflux exhaust stage group, a deaerator, and a feed water pump group connected in sequence, the intermediate pressure reflux exhaust stage group is coaxially arranged with the exhaust stage groups in the two adjacent exhaust gas heating assemblies, the deaerator is connected to the heater of the intermediate pressure cylinder located downstream, and the feed water pump group is connected to the heater of the intermediate pressure cylinder located upstream; And / or, the low-pressure cylinder includes two of the exhaust heating components and a final-stage exhaust component located downstream of the two exhaust heating components, the final-stage exhaust component includes a final-stage exhaust stage group, an air-cooled condenser and a condensate pump connected in sequence, the final-stage exhaust stage group is coaxially arranged with the exhaust stage group of the low-pressure cylinder, and the air-cooled condenser is connected to the heater of the adjacent low-pressure cylinder through the condensate pump. In some embodiments, the medium-pressure reflux extraction stage group and the air-cooled condenser are connected via a small steam turbine, and part of the working fluid at the medium-pressure reflux extraction stage group flows into the small steam turbine to drive the feed water pump group. In some embodiments, an electric valve is provided between the small steam turbine and the medium-pressure reflux extraction stage group. In some embodiments, the steam turbine unit further comprises a mixing pipeline, wherein the mixing pipeline is located between two adjacent heaters; and / or, the mixing pipeline is located between adjacent heaters and the deaerator; and / or, the mixing pipeline is located between adjacent heaters and the air-cooled condenser; The heat-exchanged working medium in the downstream heater can be mixed with the unheated working medium in any one of the upstream heater, the deaerator and the air-cooled condenser through the mixing pipeline. In some embodiments, the clutch mechanism is an electromagnetic clutch. The embodiment of the present application further provides an operating method for operating the above-mentioned boiler peak-shaving heating system, comprising the following steps: Obtaining the load status of the boiler peak-shaving heating system; When the boiler peak-shaving heating system is in a low-load state, the connection between the power generation component and the mechanical heat pump unit is cut off. According to the operating method of the boiler peak-shaving heating system in the embodiment of the present application, it is possible to determine whether to perform deep peak-shaving according to the load status of the boiler peak-shaving heating system, and when deep peak-shaving is required, the electric load of the supply grid can be reduced by connecting the above-mentioned mechanical heat pump unit to achieve rapid deep peak-shaving of the unit. This operating mode achieves precise matching of power supply and heat supply, and achieves better heating effect while achieving deep peak-shaving. BRIEF DESCRIPTION OF THE DRAWINGS In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work. FIG1 is a schematic diagram of the overall structure of a boiler peak-shaving heating system according to an embodiment of the present application; FIG2 is a schematic structural diagram of a mechanical heat pump unit in a boiler peak-shaving heating system according to an embodiment of the present application; 3 is a schematic structural diagram of an absorption heat pump unit in a boiler peak-shaving heating system according to an embodiment of the present application; FIG4 is a flow chart of a method for operating a boiler peak-shaving heating system according to an embodiment of the present application. In the picture: 1. Mechanical heat pump unit; 101. First evaporator; 102. Compressor; 103. Working fluid heat exchanger; 104. Expansion valve; 2. Absorption heat pump unit; 201. Generator; 202. High-temperature heat exchanger; 203. Second evaporator; 204. Solution mixer; 205. Low-temperature heat exchanger; 206. Solution pump; 207. Solution heat exchanger; 208. Throttle valve; 3. Power generation components; 4. Clutch mechanism; 5. Boiler unit; 6. Steam turbine unit; 61. Exhaust circuit; 611. Exhaust branch; 6111. Check valve; 6112. Electric gate valve; 612. Exhaust main Line; 613, Zhonglian regulating valve; 62, high-pressure cylinder; 63, medium-pressure cylinder; 64, low-pressure cylinder; 65, exhaust heating assembly; 651, exhaust stage group; 652, heater; 66, reheater; 67, medium-pressure reflux assembly; 671, medium-pressure reflux exhaust stage group; 672, deaerator; 673, pre-pump; 674, feed water pump; 675, small steam turbine; 676, electric valve; 68, final-stage exhaust assembly; 681, final-stage exhaust stage group; 682, air-cooled condenser; 683, condensate pump; 69, mixing line. DETAILED DESCRIPTION The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to be used to explain the present application, but should not be understood as limiting the present application. 1 to 4 , a boiler peak-shaving heating system and an operating method thereof according to an embodiment of the present application will be described below. An embodiment of the present application provides a boiler peak-shaving heating system, as shown in Figures 1 to 3, the boiler peak-shaving heating system includes a heat pump component, a power generation component 3 and a boiler component, the heat pump component includes a mechanical heat pump unit 1 and an absorption heat pump unit 2, the number of the absorption heat pump unit 2 is at least one, the mechanical heat pump unit 1 is connected to the output end of the power generation component 3 through a clutch mechanism 4, the boiler component includes a boiler unit 5 and a turbine unit 6 that are cyclically connected, the turbine unit 6 is connected to the power generation component 3 and the absorption heat pump unit 2, the heat generated by the boiler unit 5 when working is respectively transported to the power generation component 3 and the absorption heat pump unit 2 through the turbine unit 6; when the clutch mechanism 4 is in a connected state, the power generation component 3 realizes variable load through the mechanical heat pump unit 1. The boiler peak-shaving heating system can realize flexible operation of the boiler component during deep peak-shaving through the clutch mechanism 4: during the low-load operation of the power grid, the absorption heat pump unit 2 produces heat of different qualities for residential and industrial use, realizing efficient cascade utilization of energy, with high economic benefits and more environmental protection, helping to reduce energy waste, and realizing flexible adjustment of heating and power generation by changing the distribution of working fluids; when the power grid needs to change load quickly, the mechanical heat pump unit 1 can be enabled to enable the mechanical heat pump heating system to generate a large amount of low-temperature heat for residential heating, alleviating the problem of tight heating and industrial heat use in winter, and at the same time, it can quickly reduce the electrical load supplied to the power grid, realizing rapid deep peak-shaving of the unit. The boiler peak-shaving heating system can flexibly operate the unit by switching at different loads, and can respond quickly when switching from the normal period to the peak period of the power grid. By coupling the heat pump components, the response speed of the deep peak-shaving of the boiler peak-shaving heating system and the economic benefits of the unit during operation are improved. It should be noted that the heat generated by the boiler unit 5 during operation is transported to the steam turbine unit 6 in the form of working fluid, and then transported to the power generation component 3 and the absorption heat pump unit 2 respectively through one or more distributions to realize power generation and heat supply functions. Specifically, the working medium may be steam. In order to facilitate the connection between the steam turbine unit 6 and the absorption heat pump unit 2, in some embodiments, the steam turbine unit 6 and the absorption heat pump unit 2 are connected through several exhaust circuits 61, and any exhaust circuit 61 is provided with a central regulating valve 613 with adjustable opening. The central regulating valve 613 can adjust the flow of the working medium passing through by adjusting the opening, thereby adjusting the amount of steam extracted for heating. In one embodiment, the larger the opening of the central regulating valve 613, the more steam is extracted, and the better the heating effect of the absorption heat pump unit 2. In some embodiments, the exhaust circuit 61 includes several exhaust branches 611 and an exhaust main line 612. Any exhaust branch 611 is provided with a check valve 6111 and an electric gate valve 6112. All exhaust branches 611 are connected to the exhaust main line 612, and the exhaust main line 612 is connected to the absorption heat pump unit 2. The number of the aforementioned exhaust branches 611 is at least two, and can be three or even more. Generally speaking, one of the aforementioned exhaust branches 611 is connected to the main exhaust line 612, with different exhaust branches 611 connected to different locations on the steam turbine unit 6 to obtain high-temperature working fluids with varying temperatures. By selecting different exhaust branches 611, different high-temperature working fluids can be obtained, thereby enabling the output of heat sources with varying temperatures, meeting the needs of different users and achieving efficient, tiered energy utilization. The above-mentioned electric gate valve 6112 can help prevent the generated water from flowing back into the steam turbine unit 6. Specifically, since the steam pressure at the end of the exhaust circuit 61 is relatively low, when the pressure in the pipeline changes, the steam therein is easily liquefied into water and then flows back into the steam turbine unit 6. The electric gate valve 6112 and the check valve 6111 can overcome the above problem. In some embodiments, the steam turbine unit 6 includes a high-pressure cylinder 62, a medium-pressure cylinder 63 and a low-pressure cylinder 64. When connecting the steam turbine unit 6 and the absorption heat pump unit 2, one or more of the three cylinders with different pressures can be selected to be connected to the absorption heat pump unit 2. The following takes the example of the steam turbine unit 6 being connected to the absorption heat pump unit 2 via the intermediate pressure cylinder 63 to specifically describe the structure of the boiler peak load regulation heating system of this embodiment. As shown in FIG1 , the boiler assembly includes a boiler unit 5 and a steam turbine unit 6 which are connected in a circular manner. It absorbs heat and forms high-temperature and high-pressure steam, which then enters the steam turbine unit 6 to perform work.

[0054] Specifically, the steam turbine unit 6 includes a high-pressure cylinder 62, an intermediate-pressure cylinder 63 and a low-pressure cylinder 64 connected in sequence. The high-pressure cylinder 62, the intermediate-pressure cylinder 63 and the low-pressure cylinder 64 each include a plurality of exhaust heating components 65; the exhaust heating component 65 includes an exhaust stage group 651 and a heater 652, and all the exhaust stage groups 651 are arranged in sequence along the axial direction of the steam turbine unit 6; a reheater 66 is provided between the high-pressure cylinder 62 and the intermediate-pressure cylinder 63, and two adjacent exhaust stage groups 651 are connected through the reheater 66, and the low-pressure cylinder 64 is connected to the power generation component 3. Specifically, the reheater 66 reheats the working fluid, whose temperature and pressure have been reduced by work, into high-temperature, medium-pressure steam, helping to improve the thermal efficiency and heat output of the steam turbine unit 6, as shown in Figure 1. The gas flowing out of the high-pressure cylinder 62, with the exception of a small portion used for extraction, is mostly sent to the reheater 66 for heating. In some embodiments, the medium pressure cylinder 63 includes two exhaust heating components 65, and the two adjacent exhaust heating components 65 are connected through a medium pressure reflux component 67. The medium pressure reflux component 67 includes a medium pressure reflux exhaust stage group 671, a deaerator 672 and a water supply pump group connected in sequence. The medium pressure reflux exhaust stage group 671 is coaxially arranged with the exhaust stage group 651 in the two adjacent exhaust heating components 65. The deaerator 672 is connected to the heater 652 of the medium pressure cylinder 63 located downstream, and the water supply pump group is connected to the heater 652 located upstream. The heater 652 of the medium-pressure cylinder 63 is connected; and / or, the low-pressure cylinder 64 includes two exhaust heating components 65 and a final exhaust component 68 located downstream of the two exhaust heating components 65, the final exhaust component 68 includes a final exhaust stage group 681, an air-cooled condenser 682 and a condensate pump 683 connected in sequence, the final exhaust stage group 681 is coaxially arranged with the exhaust stage group 651 of the low-pressure cylinder 64, and the air-cooled condenser 682 is connected to the heater 652 of the adjacent low-pressure cylinder 64 through the condensate pump 683. Specifically, the above-mentioned water supply pump group includes a pre-pump 673 and a water supply pump 674. The two pump bodies can realize two pressurization treatments of water, thereby gradually increasing the water pressure so that the equipment can circulate better; and / or, a slag cooler is also provided between the above-mentioned condensate pump 683 and the low-pressure heater 652. In some embodiments, the medium-pressure reflux extraction stage group 671 and the air-cooled condenser 682 are connected through a small steam turbine 675, and part of the working fluid at the medium-pressure reflux extraction stage group 671 flows into the small steam turbine 675 to drive the feed water pump group. Specifically, in some embodiments, the high-pressure cylinder 62 has a two-stage exhaust heating component 65 . The high-temperature, high-pressure steam generated within the boiler unit 5 flows sequentially into the high-pressure cylinder 62, the intermediate-pressure cylinder 63, and the low-pressure cylinder 64. The steam flowing into the first-stage exhaust heating assembly 65 of the high-pressure cylinder 62 is divided into two parts: one part flows into the exhaust unit within the second-stage exhaust heating assembly 65, while the other part serves as exhaust #1, a steam source for the heater 652 within the first-stage exhaust heating assembly 65 (to provide heat). The steam flowing into the second-stage exhaust heating assembly 65 is also divided into two parts: one part enters the reheater 66 for heating, while the other part serves as exhaust #2, a steam source for the heater 652 within the second-stage exhaust heating assembly 65. After being heated by the heater 652, the steam becomes intermediate-pressure, high-temperature steam and can enter the intermediate-pressure cylinder 63 to perform work. The steam entering the intermediate pressure cylinder 63 undergoes a third exhaust treatment in the first exhaust heating component 65 and is also divided into two parts. One part flows into the intermediate pressure reflux exhaust stage group 671 in the intermediate pressure reflux component 67 through the fourth exhaust treatment, and the other part is used as exhaust #3 as the steam source for the heater 652 in the first exhaust heating component 65; part of the steam flowing into the intermediate pressure reflux component 67 flows into the deaerator 672 and the small steam turbine 675 through exhaust #4 and exhaust #5 respectively. The steam flowing into the small steam turbine 675 can be As the power source for driving the small steam turbine 675, the small steam turbine 675 can be used to drive the feed water pump group; the gas flowing into the deaerator 672 flows into the heater 652 in the exhaust heating component 65 after treatment by the feed water pump group, and can be provided for heating treatment by the heater 652; the remaining gas after the above two exhaust pumpings is also divided into two parts after flowing into the secondary exhaust heating component 65, one part of which flows out from the medium pressure cylinder 63, and the other part flows into the heater 652 of the secondary exhaust heating component 65 through exhaust #6. Part of the steam flowing out of the intermediate pressure cylinder 63 enters the low pressure cylinder 64. After passing through the first-stage exhaust heating assembly 65 and the second-stage exhaust heating assembly 65 located in the low pressure cylinder 64 (this is consistent with the above, passing through exhaust #7 and exhaust #8 in sequence, which will not be repeated here), the remaining gas flows into the final exhaust assembly 68, and the resulting exhaust steam enters the air-cooled condenser 682. After entering the air-cooled condenser 682, the exhaust steam is condensed and sent to the heater 652 in the second-stage exhaust heating assembly 65 and the heater 652 in the first-stage exhaust heating assembly 65 by the condensate pump 683, and finally flows into the heater 652 of the second-stage exhaust heating assembly 65 of the intermediate pressure cylinder 63. The water in the heater 652 in the secondary exhaust heating assembly 65 of the medium-pressure cylinder 63 is treated by the deaerator 672 and then transported to the heater 652 in the primary exhaust heating assembly 65 of the cylinder body under the action of the water supply pump group. Then, the water flows into the high-pressure cylinder 62 through the relevant pipelines and is treated by the heater 652 in the high-pressure cylinder 62 before flowing into the boiler unit 5 again. In the above-mentioned cycle process, the generated condensed water can be processed through various levels of heat absorption to form steam, and the above-mentioned work process is circulated. During the above-mentioned cyclic working process, the exhaust steam remaining after the small steam turbine 675 works will also flow into the air-cooled condenser 682 for condensation. In some embodiments, an electric valve 676 is provided between the small steam turbine 675 and the medium-pressure reflux extraction stage group 671 . In some embodiments, the steam turbine unit 6 further includes a mixing line 69, which is located between two adjacent heaters 652; and / or, the mixing line 69 is located between an adjacent heater 652 and a deaerator 672; and / or, the mixing line 69 is located between an adjacent heater 652 and an air-cooled condenser 682; the heat-exchanged working fluid in the downstream heater 652 can be mixed with the unheat-exchanged working fluid in any one of the upstream heaters 652, the deaerator 672 and the air-cooled condenser 682 through the mixing line 69. The above-mentioned mixing is used to mix the working fluid that has undergone heat exchange treatment with the working fluid of the next stage that has not undergone heat exchange treatment, which helps to achieve efficient heat exchange of the working fluid and avoid heat waste. In some embodiments, the clutch mechanism 4 is an electromagnetic clutch. The structures of the mechanical heat pump unit 1 and the absorption heat pump unit 2 are described below. The structure of the mechanical heat pump unit 1 is shown in Figure 2 and includes a first evaporator 101, a compressor 102, a working medium heat exchanger 103, and an expansion valve 104. When the unit requires rapid load change for deep peak load regulation and there is a demand for low-temperature heating, the mechanical heat pump unit 1 can consume excess electricity and generate the required heat to supply heat users. The specific measures are: Opening the electromagnetic clutch connected to the output end (i.e., the rotor) of the power generation component 3 puts the mechanical heat pump system connected thereto into operation. At this time, the system working fluid is pressurized by the compressor 102 to become a high-temperature and high-pressure working fluid, and then is cooled by the working fluid heat exchanger 103 to release heat. After further cooling by the expansion valve 104, it enters the first evaporator 101 to absorb heat, and then the working fluid flows into the compressor 102 and is turned into high-temperature and high-pressure steam through work. The above cycle repeats, with the external low-temperature working fluid passing through the working fluid heat exchanger 103, absorbing heat and becoming a low-temperature heat source for heat users. The heat pump efficiently generates heat. Simultaneously, the mechanical heat pump device directly acts on the rotor of the generator set, rapidly reducing the shaft work of the steam turbine unit 6 on the generator set, thereby achieving rapid load variation during deep peak regulation. The mechanical heat pump heating system adjusts the discharge pressure and flow of the compressor 102 to increase or decrease the heating load. In some embodiments, since the steam turbine unit 6 is connected to the absorption heat pump unit 2 via the intermediate pressure cylinder 63, as shown in FIG1 , the three different stages of the intermediate pressure cylinder 63 are all connected to the absorption heat pump unit 2 via return branches, and a central regulating valve 613 is also provided on the exhaust circuit 61. When one of the valves is open, the other valves in the pipeline are all closed. Absorption heat pump unit 2 is a lithium bromide absorption heat pump, the structure of which is shown in Figure 3. This absorption heat pump unit 2 uses steam as an external heat source, providing heat to generator 201 through a heat exchanger. This causes the steam in the lithium bromide solution therein to absorb heat and evaporate, becoming high-temperature steam. This steam enters the high-temperature heat exchanger to exchange heat with the working fluid. After passing through throttle valve 208, it becomes a low-temperature working fluid, which absorbs heat in second evaporator 203 and enters solution mixer 204. The concentrated solution formed in generator 201 releases heat through solution heat exchanger 207, passes through throttle valve 208, and mixes with the heat-absorbing water in solution mixer 204. This dilute solution then passes through low-temperature heat exchanger 205, releasing heat. After that, it enters solution heat exchanger 207 through a working fluid pump for preliminary preheating before entering generator 201, completing the cycle. The external low-temperature working fluid passes through low-temperature heat exchanger 205 and high-temperature heat exchanger 202 to become a high-temperature working fluid, which delivers heat to the user. During the heating process, the amount of steam supplied to the absorption heat pump unit 2 can be controlled by controlling the opening of the intermediate regulating valve 613. At the same time, the flow rate of the working medium can be effectively changed in conjunction with the solution pump 206 and other components, thereby changing the heat load of the heating. This absorption heat pump can generate a large amount of intermediate heat from a small amount of high-temperature heat source. Furthermore, due to its multiple extraction temperatures, it can output heat sources with different temperatures from high-temperature heat sources, thus serving users with different needs and achieving efficient cascaded energy utilization. Compared with traditional technical solutions, it has higher economic benefits and meets higher environmental protection requirements. That is to say, in some embodiments, the heating amount and heating quality of the boiler peak-shaving heating system are not only determined by the peak-shaving requirements of the power grid and the heating demand, but can also be switched and adjusted by switching pipeline valves. Of course, the types and quantities of the above-mentioned absorption heat pumps can also be flexibly adjusted according to local heating needs, so as to achieve functions such as outputting multiple grades of heat at the same time. Alternatively, the air-cooled condenser 682 and other equipment that releases heat to the outside may also be installed with a heat pump structure with a low-temperature heat absorption function to fully utilize the waste heat of the power plant. When the unit does not participate in peak regulation and there is no demand for heating, the above-mentioned exhaust circuit 61 is directly closed and the check valves 6111 and electric gate valves 6112 on all exhaust branches 611 are closed, and the opening of the central regulating valve 613 is adjusted to the maximum. At this time, the system can operate normally. It can be understood that the boiler peak-shaving heating system provided in this embodiment can provide a system that can quickly change load and increase peak-shaving depth for power generation equipment with heating demand and deep peak-shaving demand through the mechanical heat pump unit 1 and the absorption heat pump unit 2. The boiler peak-shaving heating system improves energy utilization efficiency and increases the economic efficiency of heating by coupling heat pump components. By extracting steam from different locations as the driving heat source for the absorption heat pump, different energy grades are generated, achieving cascaded energy utilization. This boiler peak-shaving heating system effectively improves the unit's flexible operation capability, enabling rapid response to grid load shifts and increasing the load response rate of the heating unit. This is of great significance for improving the service level of the power system and the economic benefits of the thermal system. The embodiment of the present application further provides an operating method for operating the above-mentioned boiler peak-shaving heating system, as shown in FIG4 , comprising the following steps: Step S1: Obtain the load status of the boiler peak-shaving heating system; Step S2: When the boiler peak-shaving heating system is in a low-load state, the connection between the power generation component 3 and the mechanical heat pump unit 1 is cut off. The operating method of the boiler peak-shaving heating system provided in the embodiment of the present application can determine whether to perform deep peak-shaving according to the load status of the boiler peak-shaving heating system, and when deep peak-shaving is required, the electric load of the supply grid can be reduced by connecting the above-mentioned mechanical heat pump unit 1, thereby realizing rapid deep peak-shaving of the unit. This operating mode realizes the precise matching of power supply and heat supply, and achieves better heating effect while achieving deep peak-shaving. Specifically, the mechanical heat pump unit 1 is mainly used for the rapid load change of the power grid. By connecting to the mechanical heat pump unit 1, low-temperature heat can be generated for residential heating, alleviating the problem of tight heating and industrial heat use in winter. In addition, the power load supplied to the power grid can be quickly reduced, realizing rapid and deep peak regulation of the boiler peak-shaving heating system. In other operating stages (low-load operation and normal allowable stages), the absorption heat pump unit 2 can obtain heat sources with different temperatures by extracting air from different parts of the steam turbine unit 6, generating medium and high temperature heat of different qualities for residential and industrial use. At this time, the boiler peak-shaving heating system can use a small amount of high-temperature heat source and generate a large amount of intermediate heat to supply different heat users, realizing efficient cascade utilization of energy, having high economic benefits, and meeting environmental protection requirements. In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of such features. Throughout the description of this application, "plurality" means at least two, for example, two, three, etc., unless otherwise specifically defined. In this application, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection, or communication; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in this application based on specific circumstances. In this application, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature. In this application, the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and the features of different embodiments or examples without contradiction. Although the embodiments of the present application have been shown and described above, it can be understood that the above embodiments are exemplary and cannot be understood as limitations on the present application. Ordinary technicians in this field can change, modify, replace and modify the above embodiments within the scope of the present application.

Claims

1. A boiler peak-shaving heating system, characterized in that: include: A heat pump assembly, the heat pump assembly comprising a mechanical heat pump unit (1) and an absorption heat pump unit (2), wherein the number of the absorption heat pump unit (2) is at least one; A power generation component (3), wherein the mechanical heat pump unit (1) is connected to the output end of the power generation component (3) via a clutch mechanism (4); A boiler assembly, comprising a boiler unit (5) and a steam turbine unit (6) in cyclic communication, wherein the steam turbine unit (6) is connected to the power generation unit (3) and the absorption heat pump unit (2), and heat generated by the boiler unit (5) during operation is respectively transported to the power generation unit (3) and the absorption heat pump unit (2) via the steam turbine unit (6); when the clutch mechanism (4) is in a connected state, the power generation unit (3) realizes load variation through the mechanical heat pump unit (1).

2. The boiler peak load regulation heating system according to claim 1, characterized in that: The steam turbine unit (6) and the absorption heat pump unit (2) are connected via a plurality of air extraction circuits (61), and any one of the air extraction circuits (61) is provided with a central regulating valve (613) with adjustable opening.

3. The boiler peak load regulation heating system according to claim 2, characterized in that: The air extraction circuit (61) comprises a plurality of air extraction branches (611) and an air extraction main line (612). Each of the air extraction branches (611) is provided with a check valve (6111) and an electric gate valve (6112). All of the air extraction branches (611) are connected to the air extraction main line (612), and the air extraction main line (612) is connected to the absorption heat pump unit (2).

4. The boiler peak load regulation heating system according to claim 1, characterized in that: The steam turbine unit (6) includes a high-pressure cylinder (62), a medium-pressure cylinder (63), and a low-pressure cylinder (64) connected in sequence, and the high-pressure cylinder (62), the medium-pressure cylinder (63), and the low-pressure cylinder (64) all include a plurality of exhaust heating components (65); The air extraction heating assembly (65) comprises an air extraction stage group (651) and a heater (652), and all the air extraction stage groups (651) are arranged in sequence along the axial direction of the steam turbine group (6); A reheater (66) is provided between the high-pressure cylinder (62) and the medium-pressure cylinder (63), and two adjacent air extraction stage groups (651) are connected via the reheater (66).

5. The boiler peak load regulation heating system according to claim 4, characterized in that: The medium-pressure cylinder (63) includes two air extraction and heating components (65), and the two adjacent air extraction and heating components (65) are connected via a medium-pressure reflux component (67). The medium-pressure reflux component (67) includes a medium-pressure reflux air extraction stage group (671), a deaerator (672), and a water supply pump group connected in sequence. The medium-pressure reflux air extraction stage group (671) is coaxially arranged with the air extraction stage group (651) in the two adjacent air extraction and heating components (65). The deaerator (672) is connected to the heater (652) of the medium-pressure cylinder (63) located downstream, and the water supply pump group is connected to the heater (652) of the medium-pressure cylinder (63) located upstream. And / or, the low-pressure cylinder (64) includes two of the exhaust heating components (65) and a final exhaust component (68) located downstream of the two exhaust heating components (65), the final exhaust component (68) includes a final exhaust stage group (681), an air-cooled condenser (682) and a condensate pump (683) connected in sequence, the final exhaust stage group (681) is coaxially arranged with the exhaust stage group (651) of the low-pressure cylinder (64), and the air-cooled condenser (682) is connected to the heater (652) of the adjacent low-pressure cylinder (64) through the condensate pump (683).

6. The boiler peak load regulation heating system according to claim 5, characterized in that: The medium-pressure reflux extraction stage group (671) and the air-cooled condenser (682) are connected via a small steam turbine (675), and part of the working fluid at the medium-pressure reflux extraction stage group (671) flows into the small steam turbine (675) to drive the feed water pump group.

7. The boiler peak load regulation heating system according to claim 6, characterized in that: An electric valve (676) is provided between the small steam turbine (675) and the medium-pressure reflux extraction stage group (671).

8. The boiler peak load regulation heating system according to any one of claims 5 to 7, characterized in that: The steam turbine unit (6) further comprises a mixing pipe (69), wherein the mixing pipe (69) is located between two adjacent heaters (652); and / or, the mixing pipe (69) is located between adjacent heaters (652) and the deaerator (672); and / or, the mixing pipe (69) is located between adjacent heaters (652) and the air-cooled condenser (682); The heat-exchanged working fluid in the downstream heater (652) can be mixed with the unheated working fluid in any one of the upstream heater (652), the deaerator (672) and the air-cooled condenser (682) through the mixing line (69).

9. The boiler peak load regulation heating system according to claim 1, characterized in that: The clutch mechanism (4) is an electromagnetic clutch.

10. A method for operating the boiler peak-shaving heating system according to any one of claims 1 to 9, characterized in that it comprises the following steps: Obtaining the load status of the boiler peak-shaving heating system; When the boiler peak-shaving heating system is in a low-load state, the connection between the power generation component (3) and the mechanical heat pump unit (1) is cut off.

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