Absorption-compression heat pump and open type compression coupling superheated steam generation system

Abstract

The invention discloses an absorption-compression heat pump and open compression coupled superheated steam generation system, and relates to the field of superheated steam generation. Comprising a compression type sub-circulation evaporator and a heat exchange pipeline thereof, a preheater and a heat exchange pipeline thereof, a generator and a heat exchange pipeline thereof, an absorption type sub-circulation evaporator and a heat exchange pipeline thereof, an absorption type sub-circulation condenser and a heat exchange pipeline thereof, an absorber and a heat exchange pipeline thereof, a heat exchanger, a solution pump, a refrigerant pump, a water pump, a first throttle valve and a second throttle valve, a refrigerant compressor, a water vapor compressor and a corresponding connecting pipeline. The absorption-compression coupling heat pump is used for extracting heat energy from air and improving the quality of the heat energy, energy consumption can be remarkably reduced, the compressor is used for increasing the steam pressure and the superheat degree, # imgabs0 # loss caused in the heat exchange process can be effectively reduced through multi-stage water supply heating, and therefore the steam generation efficiency of the system is further improved, and the energy consumption of the system is reduced. And the energy consumption for producing the superheated steam is reduced.

Description

Technical Field

[0001] The present invention relates to the field of superheated steam generation, and particularly to an absorption-compression heat pump and an open-compression coupled superheated steam generation system. Background Art

[0002] Superheated steam is widely used in industrial production. When used as a heat source, steam often needs to be transported from a steam generation device to a heat-using end through a pipeline to release heat energy. To avoid the formation of liquid droplets due to steam condensation during transportation, which may cause pipeline congestion or corrosion, it is necessary to ensure that the steam has a certain degree of superheat during production. When directly used in industrial production, superheated steam can also be used to provide an oxygen-free environment or to dry foods, etc. using its superheat. In these processes, superheated steam cannot be replaced by saturated steam. Therefore, how to efficiently produce superheated steam and precisely control its properties is an important link in promoting energy conservation, emission reduction, cost reduction, and efficiency improvement in industrial production.

[0003] Among existing water vapor evaporation devices, boilers using coal, gas, or electricity as heat sources are still the mainstream. The pollution and carbon emissions caused by the combustion of fossil fuels are relatively large, and urgent improvements are needed in environmental protection. Coal itself has a complex composition, and it is difficult to control combustion, making it difficult to maintain full combustion. The large amount of solid waste, flue gas, etc. generated by combustion also causes additional heat waste. This results in a relatively low energy efficiency of coal-fired and gas-fired boilers. In terms of the steam generation principle, when heating water under a certain pressure, the temperature remains constant during the water vapor evaporation process, and the temperature rises after complete evaporation to dry saturated steam. Therefore, directly heating with a constant-temperature heat source such as electric heating to produce superheated steam will result in too large a heat transfer temperature difference during the evaporation process, causing a large amount of irreversible losses, wasting energy, and reducing energy utilization efficiency. This makes the existing processing method of producing high-pressure superheated steam by heating high-pressure hot water with a boiler have potential for improvement in energy conservation.

[0004] In summary, the existing steam preparation method by direct boiler heating has problems in terms of environment, cost, efficiency, etc., specifically manifested as follows: 1) During the heat production process, waste gas, solid waste, etc. generated by the combustion of fossil fuels cause environmental pollution; 2) Due to the characteristics of coal-fired boilers themselves, there are large waste heat losses during the heating process, low energy utilization efficiency, and high steam production costs; 3) Using a constant-temperature heat source for heating results in a large temperature difference during the heat transfer process, causing irreversible losses and reducing the overall efficiency of the system.

[0005] Therefore, technicians in this field are committed to developing an absorption-compression heat pump and an open-compression coupled superheated steam generation system. Summary of the Invention

[0006] In view of the above defects of the prior art, the technical problem to be solved by the present invention is that the steam preparation method directly heated by a boiler has problems such as environmental pollution caused by waste gas and solid waste, large waste heat loss, low energy utilization rate, high steam production cost, and low heat exchange efficiency.

[0007] To achieve the above object, the present invention provides an absorption-compression heat pump and open compression coupled superheated steam generation system, including a compression sub-cycle evaporator and its heat exchange pipeline, a preheater and its heat exchange pipeline, a generator and its heat exchange pipeline, an absorption sub-cycle evaporator and its heat exchange pipeline, an absorption sub-cycle condenser and its heat exchange pipeline, an absorber and its heat exchange pipeline, a heat exchanger, a solution pump, a refrigerant pump, a water pump, a first throttle valve, a second throttle valve, a refrigerant compressor, a steam compressor and corresponding connecting pipelines; the connecting pipelines include a connecting pipeline between an air heat source and the heat exchanger of the compression sub-cycle evaporator, a pipeline for outputting high-pressure superheated steam after the feed water passes through a pressurizing device and a heat release device of the heat pump system, a refrigerant heat exchange pipeline in the compression sub-cycle of the refrigerant compressor, the heat exchange pipeline of the preheater, the heat exchange pipeline of the generator, the heat exchange pipeline of the absorption sub-cycle evaporator, the first throttle valve, the heat exchange pipeline of the absorption sub-cycle condenser, a refrigerant circulation pipeline between the compression sub-cycle evaporators, a solution circulation pipeline between the generator and the absorber, and a refrigerant pipeline between the generator and the absorber;

[0008] During operation, in the compression sub-cycle, the compression sub-cycle evaporator absorbs heat energy from the air through a heat exchanger. The liquid refrigerant in the compression sub-cycle evaporator absorbs heat and evaporates into gaseous refrigerant, which flows into the refrigerant compressor for compression. After being compressed by the refrigerant compressor, the high-temperature and high-pressure gaseous refrigerant sequentially flows into the preheater, the generator heat exchange pipeline, and the absorption sub-cycle evaporator heat exchange pipeline to release heat and condense into liquid state. The high-pressure liquid refrigerant reduces its pressure through the first throttle valve and flows into the absorption sub-cycle condenser heat exchange pipeline. After absorbing heat, it flows back into the compression sub-cycle evaporator again to complete the cycle process of the compression sub-cycle. In the absorption sub-cycle, the solution in the generator absorbs heat from the heat exchange pipeline to generate refrigerant vapor. The vapor flows into the absorption sub-cycle condenser and releases heat to the refrigerant in the heat exchange pipeline and condenses. The condensed liquid refrigerant is pressurized by the refrigerant pump and absorbs heat and evaporates in the absorption sub-cycle evaporator, then flows into the absorber. The concentrated solution of the absorbent after absorbing the vapor generated in the generator is pressurized by the solution pump, absorbs heat in the heat exchanger, and then flows into the absorber, absorbing the gaseous refrigerant evaporated in the absorption sub-cycle evaporator and releasing heat to the heat exchange pipeline. The dilute solution obtained after absorption releases heat through the heat exchanger, reduces its pressure through the second throttle valve, and then flows back to the generator to complete the solution cycle process of the absorption sub-cycle. The feed water is initially pressurized by the water pump, flows through the preheater heat exchange pipeline and the absorber heat exchange pipeline to absorb heat and heat up and evaporate into saturated steam, and then is compressed by the steam compressor into superheated steam at the required pressure and output.

[0009] Furthermore, in addition to the working environment temperature, the required steam output pressure, and the superheat degree, the optimization parameters that the system needs to design only include the coupling temperature of the absorption sub-cycle and the compression sub-cycle, that is, the condensation temperature of the refrigerant in the compression sub-cycle and the feed water flow rate. Other operating parameters are regulated according to the optimization parameters.

[0010] Furthermore, the regulation method of the operating parameters is specifically as follows: Determine the heat absorption of the feed water in the heat exchange pipeline of the preheater and the heat exchange pipeline of the absorber according to the coupling temperature and the feed water flow rate. Assuming the absorption temperature of the absorber as a variable, perform iterative solution according to the heat absorption of the feed water in the heat exchange pipeline of the absorber; the output pressure of the water pump is determined by the heat release temperature of the absorber, which is the saturation pressure corresponding to the steam temperature at the outlet of the absorber heat exchanger; the output pressure of the refrigerant compressor is determined by the saturation pressure of the refrigerant at the coupling temperature; the generation temperature of the generator and the evaporation temperature of the absorption sub-cycle evaporator are determined by the coupling temperature; the evaporation pressure of the absorption sub-cycle evaporator is determined by the refrigerant saturation pressure corresponding to the evaporation temperature; the concentration of the dilute solution at the outlet of the absorber of the absorption sub-cycle is determined by the absorption temperature and the evaporation pressure of the absorption sub-cycle evaporator, which is the solution saturation concentration at this temperature and pressure; the condensation pressure of the condenser of the absorption sub-cycle is determined by the saturation pressure of the refrigerant of the absorption sub-cycle corresponding to the evaporation temperature of the compression sub-cycle; the circulation ratio of the absorption sub-cycle is determined by the coupling temperature and the condensation pressure. The concentration of the concentrated solution generated can be obtained from the generation temperature of the generator and the condensation pressure of the condenser of the absorption sub-cycle. Combining with the concentration of the dilute solution, the circulation ratio can be calculated; the solution flow rate inside the absorption sub-cycle can be calculated according to the heat absorption of the generator and the absorption sub-cycle evaporator, the solution concentration, and the refrigerant pressure, where the sum of the heat absorption of the generator, the absorption sub-cycle evaporator, and the preheater is equal to the heat release of the refrigerant condensation in the compression sub-cycle; the working pressures of the refrigerant pump and the solution pump are determined by the solution concentration and the circulation ratio of the absorption sub-cycle; the pressure ratio of the steam compressor is determined by the output pressure of the water pump and the required steam output pressure.

[0011] Furthermore, the absorption sub-cycle in the absorption-compression heat pump and open-compression coupled superheated steam generation system uses an absorption refrigeration working pair as the absorbent and refrigerant, and selects one of the lithium bromide-water working pair, calcium chloride-water, and water-ammonia according to the actual cycle conditions; the refrigerant of the compression sub-cycle in the absorption-compression heat pump and open-compression coupled superheated steam generation system is selected from one of R134a, R22, and R290 according to the actual cycle conditions.

[0012] Furthermore, the system efficiency of the absorption-compression heat pump and open-compression coupled superheated steam generation system is determined by the ratio of the power increase in the internal energy of the feed water to the sum of the powers of all compressors and pumps inside the system; according to the working conditions, the required output pressure, and the superheat degree, with the system efficiency as the optimization goal, optimize the selection of the refrigerant and the refrigeration working pair, select the required equipment, and optimize the operating parameters such as the system coupling temperature and the feed water flow rate.

[0013] Further, by setting the coupling temperature of the absorption sub-cycle and the compression sub-cycle, the condensation pressure of the compression sub-cycle and the solution concentration of the absorption sub-cycle are adjusted, thereby controlling the temperature and pressure of the saturated steam at the inlet of the steam compressor; that is, according to the pressure demand and superheat demand of the output steam, the required coupling temperature can be obtained under the determined feed water flow rate setting, thereby controlling the system operation.

[0014] Further, by setting the feed water flow rate, the absorption temperature of the absorption sub-cycle can be adjusted, thereby adjusting the pressure ratio of the feed water pressurized by the water pump and the steam compressor and the circulation ratio of the absorption sub-cycle; that is, according to the pressure demand and superheat demand of the output steam, the required feed water flow rate can be obtained under the determined coupling temperature setting, thereby controlling the system operation.

[0015] Further, by synchronously adjusting the settings of the coupling temperature and the feed water flow rate, the operating pressure range of the system pressure equipment and the operating conditions of the two sub-cycles can be controlled simultaneously under the determined working conditions; that is, according to the pressure demand, superheat demand and system optimization target of the output steam, the control parameters corresponding to the optimal operating condition can be calculated.

[0016] Further, through the circulation flow rate setting, the feed water flow rate, the refrigerant flow rate of the compression sub-cycle and the solution flow rate of the absorption sub-cycle are matched; that is, during the preparation of superheated steam, the circulation ratio, the power of the refrigerant compressor and the power of the water pump are adjusted to make the condensation heat release power of the refrigerant in the compression sub-cycle match the sum of the feed water preheating power, the evaporation power and the generation power of the absorption sub-cycle, make the sum of the preheating power and the generation heat power of the generator match the feed water evaporation power, make the condensation temperature of the compression sub-cycle match the generation temperature and the evaporation temperature of the absorption sub-cycle, and make the absorption temperature of the absorption sub-cycle match the feed water evaporation temperature.

[0017] Further, the absorption-compression heat pump and the open-compression coupled superheated steam generation system further include various detection devices and a control system for measuring the air heat source, the temperature of the heat-using end, and the temperature and pressure of each device and pipeline during operation, and simultaneously adjusting the operating parameters of the system according to the pressure and superheat demand of the superheated steam.

[0018] In a preferred embodiment of the present invention, the function of the steam supply system coupled by the absorption-compression heat pump and the open compression is to utilize the air source heat energy to supply superheated steam by inputting a small amount of electric power.

[0019] When this system is used to produce high-pressure superheated steam, it absorbs heat energy from the air through the evaporator, uses the compression sub-cycle to improve the heat energy quality, preliminarily heats the feed water, and provides the absorption sub-cycle with the heat energy required for evaporation and the cold source required for condensation and heat dissipation. The generator and evaporator of the absorption sub-cycle absorb heat energy from the compression sub-cycle to further improve the heat energy quality, and release heat to the absorber heat exchange pipeline through the absorption process to complete the heating and evaporation of the feed water. The low-temperature waste heat generated is recovered by the compression sub-cycle for refrigerant evaporation. After the feed water is preliminarily pressurized by the water pump, it absorbs heat from the compression sub-cycle through the preheater heat exchange pipeline to increase the temperature, and then evaporates into saturated steam through the absorber heat exchange pipeline, and finally pressurizes by the water vapor compressor to reach the required output pressure and superheat.

[0020] The present invention utilizes an absorption-compression coupled heat pump to extract heat energy from an air source and improve the quality of the heat energy, thereby increasing the heat production and generating heat energy equivalent to more than one times the input electrical energy, thereby reducing energy consumption. The steam compressor is used to increase the temperature and pressure of the steam, and compression is used to avoid heat exchange losses, thereby achieving precise control of pressure and superheat. Liquid water absorbs heat from the heat release end of the coupled heat pump, and multi-stage heating and temperature increase generates saturated steam. The saturated steam is pressurized by a water vapor compressor to achieve the required output pressure and superheat.

[0021] Compared with the prior art, the present invention has the following beneficial technical effects:

[0022] 1. This system uses a composite heat pump to improve the quality of thermal energy. Compared with existing boiler systems, it can significantly reduce energy consumption and use clean electricity to reduce carbon emissions and environmental pollution.

[0023] 2. Using a compressor to increase steam pressure and superheat can effectively reduce the heat caused by the heat exchange process. The system reduces the loss of steam generation, thereby further improving the steam generation efficiency of the system. The irreversible loss caused by heat exchange is reduced by multi-stage heating of feed water, and the pressurization and heating process is completed by using a water vapor compressor, which reduces the energy consumption of producing superheated steam and achieves the purpose of energy conservation, emission reduction and production cost reduction.

[0024] 3. Adjust the internal coupling parameters of the system so that the output pressure and superheat can be finely controlled, thereby obtaining more accurate control results.

[0025] The concept, specific structure and technical effects of the present invention will be further described below in conjunction with the accompanying drawings to fully understand the purpose, characteristics and effects of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 is a schematic diagram of an absorption-compression heat pump and an open compression coupled superheated steam generating system according to an embodiment of the present invention;

[0027] Wherein: 1 - Compression sub-cycle evaporator and its heat exchange pipeline; 2 - Preheater and its heat exchange pipeline; 3 - Generator and its heat exchange pipeline; 4 - Absorption sub-cycle evaporator and its heat exchange pipeline; 5 - Absorption sub-cycle condenser and its heat exchange pipeline; 6 - Absorber and its heat exchange pipeline; 7 - Heat exchanger; P1 - Solution pump; P2 - Refrigerant pump; P3 - Water pump; V1 - First throttle valve; V2 - Second throttle valve; C1 - Refrigerant compressor; C2 - Steam compressor; in - Feed water end; out - Steam output end. Detailed implementation manners

[0028] The following introduces multiple preferred embodiments of the present invention with reference to the accompanying drawings of the specification to make its technical content clearer and easier to understand. The present invention can be embodied in many different forms of embodiments, and the protection scope of the present invention is not limited to the embodiments mentioned in the text.

[0029] In the drawings, components with the same structure are denoted by the same numerical labels, and components with similar structures or functions everywhere are denoted by similar numerical labels. The size and thickness of each component shown in the drawings are arbitrarily shown, and the present invention does not limit the size and thickness of each component. To make the drawings clearer, the thickness of some parts in the drawings is appropriately exaggerated.

[0030] As Figure 1 shown, it is a schematic diagram of an absorption-compression heat pump and open-compression coupled superheated steam generation system provided by the present invention. This system absorbs low-temperature heat energy from the air source, improves the quality of the heat energy through a multi-stage heat pump, provides phase change heat for the feed water, and then pressurizes it through a compressor to reach the required pressure and superheat degree, realizing the function of efficiently supplying high-pressure superheated steam.

[0031] The absorption-compression heat pump and the open-compression coupled superheated steam generation system include: a compression sub-cycle evaporator and its heat exchange pipeline 1; a preheater and its heat exchange pipeline 2; a generator and its heat exchange pipeline 3; an absorption sub-cycle evaporator and its heat exchange pipeline 4; an absorption sub-cycle condenser and its heat exchange pipeline 5; an absorber and its heat exchange pipeline 6; a heat exchanger 7; a solution pump P1; a refrigerant pump P2; a water pump P3; a first throttle valve V1, a second throttle valve V2; a refrigerant compressor C1; a steam compressor C2 and corresponding connecting pipelines. The connecting pipelines of the open multi-stage heat pump superheated steam generation system include: the connecting pipeline between the air heat source and the heat exchanger 1 of the compression sub-cycle evaporator; the pipeline for outputting high-pressure superheated steam after the feed water passes through the pressurizing equipment and the heat release equipment of the heat pump system, and the feed water in flows through the water pump P3, the heat exchange pipeline 2 of the preheater, the heat exchange pipeline 6 of the absorber and the steam compressor C2 in sequence and then outputs out; the refrigerant circulation pipeline in the compression sub-cycle including the compressor C1, the preheater 2, the heat exchange pipeline 3 of the generator, the heat exchange pipeline 4 of the absorption sub-cycle evaporator, the throttle valve V1, the heat exchange pipeline 5 of the absorption sub-cycle condenser, and the compression sub-cycle evaporator 1; the solution circulation pipeline between the generator 3 and the absorber 6, the concentrated solution flows from the generator 3 through the solution pump P1 and the heat exchanger 7 into the absorber 6 in sequence, and the dilute solution flows from the absorber 6 through the heat exchanger 7 and the second throttle valve V2 into the generator 3 in sequence; the refrigerant pipeline between the generator 3 and the absorber 6, the refrigerant flows from the generator 3 through the absorption sub-cycle condenser 5, the refrigerant pump P2, and the absorption sub-cycle evaporator 4 in sequence and then into the absorber 6.

[0032] During operation, in the compression sub-cycle, the compression sub-cycle evaporator 1 absorbs heat energy from the air through a heat exchanger. The liquid refrigerant in the compression sub-cycle evaporator 1 absorbs heat and evaporates into gaseous refrigerant, which then flows into the refrigerant compressor C1 for compression. After being compressed by the refrigerant compressor C1, the high-temperature and high-pressure gaseous refrigerant flows successively into the preheater 2, the generator heat exchange pipeline 3, and the absorption sub-cycle evaporator heat exchange pipeline 4 to release heat and condense into liquid state. The high-pressure liquid refrigerant reduces its pressure through the first throttle valve V1 and flows into the absorption sub-cycle condenser heat exchange pipeline 5. After absorbing heat, it flows back into the compression sub-cycle evaporator 1 again to complete the cycle process of the compression sub-cycle. In the absorption sub-cycle, the solution in the generator 3 absorbs heat from the heat exchange pipeline to generate refrigerant vapor. The vapor flows into the absorption sub-cycle condenser 5 and releases heat to the refrigerant in the heat exchange pipeline to condense. The condensed liquid refrigerant is pressurized by the refrigerant pump P2 and absorbs heat and evaporates in the absorption sub-cycle evaporator 4, then flows into the absorber 6. The concentrated absorbent solution in the generator 3 after generating vapor is pressurized by the solution pump P1, absorbs heat in the heat exchanger 7, and then flows into the absorber 6, where it absorbs the gaseous refrigerant evaporated in the absorption sub-cycle evaporator 4 and releases heat to the heat exchange pipeline. The dilute solution obtained after absorption releases heat through the heat exchanger 7, reduces its pressure through the second throttle valve V2, and then flows back to the generator 3 to complete the solution cycle process of the absorption sub-cycle. The feed water in is initially pressurized by the water pump P3, flows through the preheater heat exchange pipeline 2 and the absorber heat exchange pipeline 6 to absorb heat and be heated to evaporate into saturated steam, and then is compressed by the steam compressor C2 into superheated steam at the required pressure and output out.

[0033] The control method of operating parameters is specifically as follows: Determine the heat absorption of feed water in the heat exchange pipeline 2 of the preheater and the heat exchange pipeline 6 of the absorber according to the coupling temperature and the feed water flow rate. Assume the absorption temperature of the absorber 6 as a variable and perform iterative solution according to the heat absorption of the feed water in the heat exchange pipeline of the absorber; The output pressure of the water pump P3 is determined by the heat release temperature of the absorber 6 and is the saturation pressure corresponding to the steam temperature at the outlet of the absorber heat exchanger 6; The output pressure of the refrigerant compressor C1 is determined by the saturation pressure of the refrigerant corresponding to the coupling temperature; The generation temperature of the generator 3 and the evaporation temperature of the absorption sub-cycle evaporator 4 are determined by the coupling temperature; The evaporation pressure of the absorption sub-cycle evaporator 4 is determined by the saturation pressure of the refrigerant corresponding to the evaporation temperature; The concentration of the dilute solution at the outlet of the absorber 6 of the absorption sub-cycle is determined by the absorption temperature and the evaporation pressure of the absorption sub-cycle evaporator 4 and is the solution saturation concentration at this temperature and pressure; The condensation pressure of the absorption sub-cycle condenser 5 is determined by the saturation pressure of the refrigerant of the absorption sub-cycle corresponding to the evaporation temperature of the compression sub-cycle; The circulation ratio of the absorption sub-cycle is determined by the coupling temperature and the condensation pressure. The concentration of the concentrated solution generated can be obtained from the generation temperature of the generator 3 and the condensation pressure of the absorption sub-cycle condenser 5, and the circulation ratio can be calculated by combining the concentration of the dilute solution; The solution flow rate inside the absorption sub-cycle can be calculated according to the heat absorption of the generator 3 and the absorption sub-cycle evaporator 4, the solution concentration, and the refrigerant pressure. The sum of the heat absorption of the generator 3, the absorption sub-cycle evaporator 4, and the preheater 2 is equal to the heat release of the refrigerant condensation in the compression sub-cycle; The working pressures of the refrigerant pump P2 and the solution pump P1 are determined by the solution concentration and the circulation ratio of the absorption sub-cycle; The pressure ratio of the steam compressor C2 is determined by the output pressure of the water pump P3 and the required steam output pressure.

[0034] The preferred specific embodiments of the present invention have been described in detail above. It should be understood that those of ordinary skill in the art can make many modifications and variations according to the concept of the present invention without creative work. Therefore, all technical solutions that can be obtained by those skilled in the art in the technical field of the present invention based on the concept of the present invention through logical analysis, reasoning, or limited experiments on the basis of the prior art should fall within the protection scope determined by the claims.

Claims

1. An absorption-compression heat pump coupled with an open compression superheated steam generating system, characterized in that: The invention comprises a compression sub-circulation evaporator and a heat exchange pipeline (1), a preheater and a heat exchange pipeline (2), a generator and a heat exchange pipeline (3), an absorption sub-circulation evaporator and a heat exchange pipeline (4), an absorption sub-circulation condenser and a heat exchange pipeline (5), an absorber and a heat exchange pipeline (6), a heat exchanger (7), a solution pump (P1), a refrigerant pump (P2), a water pump (P3), a first throttle valve (V1), a second throttle valve (V2), a refrigerant compressor (C1), a water vapor compressor (C2) and corresponding connecting pipelines; the connecting pipeline comprises a heat source between the air and the heat exchanger (1) of the compression sub-circulation evaporator. the connecting pipeline of the heat pump system, the pipeline for feeding water to output high-pressure superheated water vapor through the pressurizing device and the heat release device of the heat pump system, the heat exchange pipeline of the refrigerant compressor (C1) in the compression sub-cycle, the heat exchange pipeline of the preheater (2), the heat exchange pipeline of the generator (3), the heat exchange pipeline of the absorption sub-cycle evaporator (4), the first throttle valve (V1), the heat exchange pipeline of the absorption sub-cycle condenser (5), the refrigerant circulation pipeline between the compression sub-cycle evaporator (1), the solution circulation pipeline between the generator (3) and the absorber (6), and the refrigerant pipeline between the generator (3) and the absorber (6); During operation, in the compression sub-cycle, the compression sub-cycle evaporator (1) absorbs heat energy from the air through the heat exchanger, and the liquid refrigerant in the compression sub-cycle evaporator (1) absorbs heat and evaporates into gaseous refrigerant, which flows into the refrigerant compressor (C1) for compression; after being compressed by the refrigerant compressor (C1), the high-temperature and high-pressure gaseous refrigerant flows into the preheater (2), the generator heat exchange pipeline (3), and the absorption sub-cycle evaporator heat exchange pipeline (4) in sequence to release heat and condense into a liquid state; the high-pressure liquid refrigerant reduces its pressure through the first throttle valve (V1), flows into the absorption sub-cycle condenser heat exchange pipeline (5), and after absorbing heat, flows into the compression sub-cycle evaporator (1) again, completing the compression sub-cycle cycle process; and in the absorption sub-cycle, the solution in the generator (3) absorbs heat from the heat exchange pipeline to generate refrigerant vapor, which flows into the absorption sub-cycle condenser (5). The refrigerant in the heat exchange pipeline releases heat and condenses; the condensed liquid refrigerant is pressurized by the refrigerant pump (P2), absorbs heat and evaporates in the absorption sub-circulation evaporator (4), and flows into the absorber (6); the absorbent concentrated solution after generating steam in the generator (3) is pressurized by the solution pump (P1), absorbs heat in the heat exchanger (7), and flows into the absorber (6), absorbs the gaseous refrigerant evaporated in the absorption sub-circulation evaporator (4) and releases heat to the heat exchange pipeline; the absorbed dilute solution releases heat through the heat exchanger (7), and flows back to the generator (3) after the pressure is reduced by the second throttle valve (V2), completing the solution circulation process of the absorption sub-circulation; the feed water is initially pressurized by the water pump (P3), flows through the preheater heat exchange pipeline (2), the absorber heat exchange pipeline (6), absorbs heat and heats up and evaporates into saturated steam, and is compressed to superheated steam of the required pressure by the water vapor compressor (C2), and outputs.

2. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: In addition to the working environment temperature and the required steam output pressure and superheat, the optimization parameters that need to be designed for the system only include the coupling temperature of the absorption sub-cycle and the compression sub-cycle, that is, the condensation temperature of the refrigerant in the compression sub-cycle and the feed water flow rate. Other operating parameters are controlled according to the optimization parameters.

3. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 2, characterized in that: The control method of the operating parameters is specifically as follows: the heat absorption of the feed water in the preheater heat exchange pipeline (2) and the absorber heat exchange pipeline (6) is determined according to the coupling temperature and the feed water flow, the absorption temperature of the absorber (6) is assumed as a variable, and the heat absorption of the feed water in the absorber heat exchange pipeline is iteratively solved; the output pressure of the water pump (P3) is determined by the heat release temperature of the absorber (6), which is the saturation pressure corresponding to the outlet steam temperature of the absorber heat exchanger (6); the output pressure of the refrigerant compressor (C1) is determined by the saturation pressure of the refrigerant corresponding to the coupling temperature; the generation temperature of the generator (3) and the evaporation temperature of the absorption sub-cycle evaporator (4) are determined by the coupling temperature; the evaporation pressure of the absorption sub-cycle evaporator (4) is determined by the saturation pressure of the refrigerant corresponding to the evaporation temperature; the concentration of the dilute solution at the outlet of the absorber (6) of the absorption sub-cycle is determined by the absorption temperature and the evaporation pressure of the absorption sub-cycle evaporator (4), which is the saturation concentration of the solution at the temperature and pressure; The condensing pressure of the absorption sub-cycle condenser (5) is determined by the saturation pressure of the absorption sub-cycle refrigerant corresponding to the evaporation temperature of the compression sub-cycle; the circulation ratio of the absorption sub-cycle is determined by the coupling temperature and the condensing pressure, the concentration of the generated concentrated solution can be obtained by the generation temperature of the generator (3) and the condensing pressure of the absorption sub-cycle condenser (5), and the circulation ratio can be calculated in combination with the concentration of the dilute solution; the solution flow rate inside the absorption sub-cycle can be calculated based on the heat absorption of the generator (3) and the absorption sub-cycle evaporator (4) and the solution concentration and the refrigerant pressure, wherein the sum of the heat absorption of the generator (3), the absorption sub-cycle evaporator (4) and the preheater (2) is equal to the heat release of the refrigerant condensation in the compression sub-cycle; the working pressures of the refrigerant pump (P2) and the solution pump (P1) are determined by the absorption sub-cycle solution concentration and the circulation ratio; the pressure ratio of the water vapor compressor (C2) is determined by the output pressure of the water pump (P3) and the required steam output pressure.

4. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: The absorption sub-cycle in the absorption-compression heat pump and the open compression coupled superheated steam generating system adopts an absorption refrigeration working medium pair as the absorbent and the refrigerant, and one of the lithium bromide-water working medium pair, calcium chloride-water, and water-ammonia is selected according to the actual cycle working conditions; the refrigerant of the compression sub-cycle in the absorption-compression heat pump and the open compression coupled superheated steam generating system is selected from one of R134a, R22, and R290 according to the actual cycle working conditions.

5. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: The system efficiency of the absorption-compression heat pump and the open compression coupled superheated steam generating system is determined by the ratio of the increased power of the internal energy of the feed water to the sum of the power of all compressors and pumps in the system; based on the working conditions and the required output pressure and superheat, the system efficiency is taken as the optimization goal, the refrigerant and the refrigerant are optimized, the required equipment is selected, and the operating parameters such as the system coupling temperature and the feed water flow rate are optimized.

6. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: By setting the coupling temperature of the absorption sub-cycle and the compression sub-cycle, the condensation pressure of the compression sub-cycle and the solution concentration of the absorption sub-cycle are adjusted, thereby controlling the temperature and pressure of the saturated steam at the inlet of the water vapor compressor (C2); that is, according to the pressure requirement and superheat requirement of the output steam, the required coupling temperature can be obtained under a determined feed water flow setting, thereby controlling the operation of the system.

7. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: By setting the feed water flow rate, the absorption temperature of the absorption sub-cycle can be adjusted, thereby adjusting the pressure ratio of the feed water pressurized by the water pump (P3) and the water vapor compressor (C2) and the circulation ratio of the absorption sub-cycle; that is, according to the pressure requirement and superheat requirement of the output steam, the required feed water flow rate can be obtained under a determined coupling temperature setting, thereby controlling the operation of the system.

8. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: By synchronously adjusting the settings of the coupling temperature and feed water flow, the operating pressure range of the system pressure equipment and the operating conditions of the two sub-cycles can be controlled simultaneously under certain working conditions; that is, based on the output steam pressure requirement, superheat requirement and system optimization objectives, the control parameters corresponding to the optimal operating conditions can be calculated.

9. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: By setting the circulation flow, the feed water flow, the compression sub-circulation refrigerant flow and the absorption sub-circulation solution flow are matched; that is, in the process of preparing superheated steam, the circulation ratio, the power of the refrigerant compressor (C1) and the power of the water pump (P3) are adjusted so that the compression sub-circulation refrigerant condensation heat release power matches the sum of the feed water preheating power, the absorption sub-circulation evaporation power and the generating power, the sum of the preheating power and the heat generating power of the generator (3) matches the feed water evaporation power, the compression sub-circulation condensation temperature matches the absorption sub-circulation generating temperature and evaporation temperature, and the absorption sub-circulation absorption temperature matches the feed water evaporation temperature.

10. The absorption-compression heat pump and open compression coupled superheated steam generation system according to claim 1, characterized in that: The absorption-compression heat pump and open compression coupled superheated steam generating system also includes various detection devices and control systems for measuring the air heat source, the temperature of the heat-using end, and the temperature and pressure of each device and pipeline during operation, and adjusting the various operating parameters of the system according to the pressure and superheat requirements of the superheated steam.

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