Steam generating system and method of operation

Abstract

The application provides a steam generation system and an operation method. The steam generation system comprises a mixed evaporator, a steam circulation system, a working medium circulation system and a measurement and control assembly. The steam generation system comprises the mixed evaporator. The measurement and conversion of the indirect signal in the steam generation system by the measurement and control assembly can measure and distribute the steam generated by mixing the liquid working medium and the gaseous working medium in the mixed evaporator, so that the mass flow rates of the steam entering the steam circulation system and the working medium circulation system are equal to the mass flow rates of the liquid working medium and the gaseous working medium before mixing, respectively. Therefore, compared with the partition wall heat exchanger in the related art, the steam generation system can significantly reduce the cost and realize accurate distribution of the flow after mixing.

Description

Technical Field

[0001] This application relates to the field of evaporative heat exchange technology, and in particular to a steam generation system and its operation method. Background Technology

[0002] Heat exchangers are fundamental thermal engineering equipment, playing a vital role in chemical, power, and many other industrial production processes. Evaporators are an important type, transferring heat from a high-temperature fluid to a low-temperature fluid, ultimately causing the low-temperature fluid to evaporate and undergo a phase change to form steam. A mixing steam generator is a special type of evaporator where two different phases of the same working fluid are mixed and exchange heat within the generator, ultimately forming steam with identical state parameters. The two phases are typically gaseous and liquid, with approximately equal pressures. The gaseous working fluid is in a superheated state. After mixing, the two working fluids undergo a heat and mass transfer process, with the gaseous working fluid directly transferring heat to the liquid working fluid, causing it to undergo a phase change.

[0003] The advantage of hybrid steam generators is a significant reduction in the amount of metal material used in heat exchangers. This is because typical heat exchangers are indirect-walled, where the two heat exchange fluids do not contact each other. To perform the heat transfer process, metal materials must be used to form heat transfer walls. Liquid evaporation must overcome a large amount of latent heat, so evaporators typically have very large areas and consume a large amount of metal material. Hybrid steam generators can be used in combined cycle power generation systems to improve the overall cycle's power generation efficiency. However, because steam is easily compressible, its flow rate cannot be accurately measured. Therefore, large-scale application of hybrid steam generators requires addressing the flow distribution problem after the two fluids mix and exchange heat; otherwise, significant flow deviations will directly affect the overall stability and economy of the system. Summary of the Invention

[0004] This application aims to at least partially solve one of the technical problems in the related art. Therefore, the purpose of this application is to propose a steam generation system and its operation method, wherein the steam generation system includes a mixing evaporator, and through measurement and control components, indirect signals in the steam generation system are measured and converted to measure and distribute the steam generated by mixing liquid and gaseous working fluids in the mixing evaporator, such that the steam mass flow rates entering the steam circulation system and the working fluid circulation system are respectively equal to the mass flow rates of the liquid and gaseous working fluids before mixing.

[0005] According to the first aspect of this application, a steam generating system is provided, comprising:

[0006] A hybrid evaporator is used to combine superheated steam and liquid working fluid that are simultaneously input into the same working fluid to generate steam.

[0007] A steam circulation system comprising a steam circulation path consisting of the hybrid evaporator, the hot side of the first heat exchanger, and a first user;

[0008] The working fluid circulation system includes a working fluid circulation loop system and a heat exchange bypass system; wherein the working fluid circulation loop system includes a working fluid circulation path consisting of the mixing evaporator, the hot side of the second heat exchanger, and the second user; the heat exchange bypass system includes a heat exchange bypass consisting of the second user output terminal, the cold side of the second heat exchanger, and the cold side of the first heat exchanger; and

[0009] A measurement and control assembly includes a control valve group and a measurement component; wherein the measurement component is used to measure the working fluid temperature, pressure and mass flow rate at multiple measurement points in the steam circulation path, the working fluid circulation path and the heat exchange bypass; the control valve group is used to control the mass flow rate of the working fluid in each path.

[0010] In some embodiments, measurement points are distributed on the pipelines between the hybrid evaporator, the hot side of the first heat exchanger, and the first user; the control valve group includes a third control valve located at the input end of the first user.

[0011] In some embodiments, a first pressure measuring point and a first temperature measuring point are included between the output end of the hybrid evaporator and the input end of the hot side of the first heat exchanger; a second temperature measuring point is included between the output end of the hot side of the first heat exchanger and the input end of the first user; and a second pressure measuring point and a third temperature measuring point are included between the output end of the first user and the input end of the hybrid evaporator.

[0012] In some embodiments, in the working fluid circulation path, a fourth temperature measuring point is included between the output end of the hot side of the second heat exchanger and the input end of the second user; a flow measuring point, a fifth temperature measuring point, and a third pressure measuring point are included between the output end of the second user and the input end of the mixing evaporator; the control valve group includes a second control valve located at the input end of the second user.

[0013] In some embodiments, the heat exchange bypass is connected in parallel between the output terminal of the second user and the flow measurement point in the working fluid circulation path; in the heat exchange bypass, an eighth temperature measurement point, a sixth temperature measurement point, and a seventh temperature measurement point are sequentially provided between the output terminal of the second user and the input terminal of the cold side of the second heat exchanger, between the output terminal of the cold side of the second heat exchanger and the input terminal of the cold side of the first heat exchanger, and at the output terminal of the cold side of the first heat exchanger.

[0014] In some embodiments, the control valve assembly includes a first control valve located at the output of the second user.

[0015] In some embodiments, a method for operating a steam generating system is provided according to the second aspect of this application, comprising operating the steam generating system described in any of the above embodiments, including...

[0016] The measuring components are used to obtain the working fluid temperature, pressure and mass flow rate values ​​at multiple measuring points in the steam circulation path, working fluid circulation path and heat exchange bypass;

[0017] The steam flow rates in the steam circulation path and the working fluid circulation path are adjusted using the second and third control valves so that t2, t4, t6, t7, and t8 conform to the formula:

[0018] To ensure that the mass flow rate of steam at the input and output ends of the first and second users are equal;

[0019] Where p1, p2, and p3 are the pressure values ​​(Pa) of the first, second, and third pressure measuring points, respectively; t1, t2, t3, t4, t5, t6, t7, and t8 are the temperature values ​​(°C) of the first, second, third, fourth, fifth, sixth, seventh, and eighth temperature measuring points, respectively; and m0 is the mass flow rate (kg / s) of the flow measuring point; m u The mass flow rate of the output steam for the first user is expressed in kg / s; the thermodynamic specific enthalpy of the working fluid is represented by the function h(t,p).

[0020] In some embodiments,

[0021] The mass flow rate of the liquid working fluid at the output end of the second user is measured by a flow meter and denoted by m0. The mass flow rate of the vapor working fluid at the output end of the first user is unknown and denoted by m. u The thermodynamic specific enthalpy of the working fluid is expressed using the function h(t,p), m u The ratio to m0 is:

[0022]

[0023] use The mass flow rate of the vapor working fluid at the output end of the first user is calculated, and adjusted by the second control valve and the third control valve to achieve the same mass flow rate of steam at the input and output ends of the first and second users.

[0024] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0025] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the following description of the embodiments taken in conjunction with the accompanying drawings, wherein:

[0026] Figure 1 This is a schematic diagram of the structure of a steam generation system according to an embodiment of this application;

[0027] Figure 2 This is a flowchart of the operation method of a steam generation system according to an embodiment of this application;

[0028] In the diagram, 1 is a mixing evaporator; 2 is the first user; 3 is the second user; 4 is the first heat exchanger; 5 is the second heat exchanger; 6 is the first pressure measuring point; 7 is the first temperature measuring point; 8 is the second temperature measuring point; 9 is the second pressure measuring point; 10 is the third temperature measuring point; 11 is the fourth temperature measuring point; 12 is the flow measuring point; 13 is the fifth temperature measuring point; 14 is the third pressure measuring point; 15 is the sixth temperature measuring point; 16 is the seventh temperature measuring point; 17 is the first control valve; 18 is the second control valve; 19 is the third control valve; and 20 is the eighth temperature measuring point. Detailed Implementation

[0029] The embodiments of this application are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application. Rather, the embodiments of this application include all variations, modifications, and equivalents falling within the spirit and scope of the appended claims.

[0030] Examples of this application are described in detail below, with examples shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The examples described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0031] According to the first aspect of this application, a steam generation system is proposed, comprising a mixing evaporator 1, a steam circulation system, a working fluid circulation system, and a measurement and control component; wherein the mixing evaporator 1 is a mixing steam generator, which is a special type of evaporator used to mix and exchange heat between two different phases of the same working fluid in the generator to ultimately form steam with the same state parameters. It is understood that the two different phases of the same working fluid entering the mixing evaporator 1 are a gaseous working fluid and a liquid working fluid, wherein the gaseous working fluid is in a superheated state. After mixing with the liquid working fluid, through a heat and mass transfer process, the gaseous working fluid directly transfers heat to the liquid working fluid, causing it to undergo a phase change and generate steam.

[0032] The steam circulation system comprises a steam circulation path consisting of a mixing evaporator 1, the hot side of a first heat exchanger 4, and a first user 2. In other words, the steam circulation system includes a steam circulation path in which the output end of the mixing evaporator 1 is connected to the input end of the hot side of the first heat exchanger 4; the output end of the hot side of the first heat exchanger 4 is connected to the input end of the first user 2; and the output end of the first user 2 is connected to the input end of the mixing evaporator 1. In the steam circulation path, the steam output from the mixing evaporator 1 is slightly cooled by the hot side of the first heat exchanger 4, then passes through the first user 2 to generate superheated steam, which enters the inlet of the mixing evaporator 1 and then returns to the first user 2.

[0033] The working fluid circulation system includes a working fluid circulation loop system and a heat exchange bypass system. The working fluid circulation loop system comprises a working fluid circulation path consisting of a mixing evaporator 1, the hot side of a second heat exchanger 5, and a second user 3. In other words, the working fluid circulation loop system includes a working fluid circulation path in which the output of the mixing evaporator 1 is connected to the input of the hot side of the second heat exchanger 5; the output of the hot side of the second heat exchanger 5 is connected to the input of the second user 3; and the output of the second user 3 is connected to the input of the mixing evaporator 1. The steam entering the working fluid circulation path is output from the mixing evaporator 1, slightly cooled by the hot side of the second heat exchanger 5, and then becomes liquid working fluid after passing through the second user 3. The liquid working fluid then enters the inlet of the mixing evaporator 1 and returns to the second user 3. Therefore, in this embodiment, the steam generated in the mixing evaporator 1 is divided into two parts: one part enters the steam circulation path, and the other part enters the working fluid circulation loop system.

[0034] In this embodiment, the working fluid circulation system also includes a heat exchange bypass system, which comprises the output end of the second user 3, the cold side of the second heat exchanger 5, and the cold side of the first heat exchanger 4. In other words, the output end of the second user 3 is connected to the cold side input end of the second heat exchanger 5, the cold side output end of the second heat exchanger 5 is connected to the cold side input end of the first heat exchanger 4, and the cold side output end of the first heat exchanger 4 is connected to the input end of the mixing evaporator 1. The two ends of the heat exchange bypass are connected in parallel to the working fluid circulation path. A large portion of the liquid working fluid at the output end of the second user 3 directly enters the mixing evaporator 1, while a small portion sequentially enters the cold side of the second heat exchanger 5 and the cold side of the first heat exchanger 4 to absorb the heat released by the steam from the hot side of the second heat exchanger 5 and the hot side of the first heat exchanger 4, raising their temperature. The heated liquid working fluid then enters the mixing evaporator 1.

[0035] Furthermore, the hybrid evaporator 1 can be used in a combined cycle power generation system to improve the overall cycle's power generation efficiency. Since steam is easily compressible, making accurate flow measurement difficult, large-scale application of the hybrid steam generator necessitates addressing the flow distribution problem after heat exchange between the two fluids. Otherwise, significant flow deviations will directly impact the overall system stability and economy. The steam generation system in this application also includes a measurement and control component. Through the regulation of this component, the mass flow rates of the gaseous working fluid at the input and output ends of the first user 2 are equal, as are the mass flow rates of the gaseous working fluid at the input end and the liquid working fluid at the output end of the second user 3.

[0036] The measurement and control components include multiple control valve assemblies and measurement units. The measurement units measure the working fluid temperature, pressure, and mass flow rate at multiple measurement points in the steam circulation path, working fluid circulation path, and heat exchange bypass. The control valve assemblies control the mass flow rate of the working fluid in each path. In other words, multiple measurement points are set in the steam circulation path, working fluid circulation path, and heat exchange bypass; the measurement units measure the working fluid temperature, pressure, and mass flow rate at each measurement point; and the control valve assemblies control the mass flow rate of the working fluid in the steam circulation path, working fluid circulation path, and heat exchange bypass.

[0037] In summary, in this embodiment, the first heat exchanger 4 and the second heat exchanger 5 convert the measurement of steam mass flow rate into the measurement of temperature, thereby achieving controlled distribution of steam flow rate in the mixing evaporator 1 and the output steam flow rate of the mixing evaporator 1. The steam mass flow rates entering the steam circulation system and the working fluid circulation system are respectively equal to the mass flow rates of the liquid and gaseous working fluids before mixing. Therefore, this application can accurately distribute the steam flow rate after mixing in the mixing evaporator 1 by measuring and converting indirect signals. Compared with indirect heat exchangers, the mixing evaporator 1 can save a large amount of metal materials in the steam generation system, and has broad application prospects in combined cycle systems.

[0038] In some embodiments, measurement points are distributed on the pipelines between the hybrid evaporator 1, the hot side of the first heat exchanger 4, and the first user 2; the control valve group includes a third control valve 19 located at the input end of the first user 2.

[0039] The system includes a first pressure measuring point 6 and a first temperature measuring point 7 between the output end of the mixing evaporator 1 and the input end of the hot side of the first heat exchanger 4; a second temperature measuring point 8 between the output end of the hot side of the first heat exchanger 4 and the input end of the first user 2; a second pressure measuring point 9 and a third temperature measuring point 10 between the output end of the first user 2 and the input end of the mixing evaporator 1; and a third control valve 19 is provided at the input end of the first user 2. An example is shown below. Figure 1As shown, the steam output from the mixing evaporator 1 passes sequentially through a first pressure measuring point 6, a first temperature measuring point 7, a second temperature measuring point 8, a third control valve 19, a second pressure measuring point 9, and a third temperature measuring point 10 in the steam circulation path. The measuring components can measure the pressure values ​​at each of the first pressure measuring points 6 and 9, and the temperature values ​​at the first temperature measuring points 7, 8, and 10. Simultaneously, the third control valve 19 is used to control the steam mass flow rate entering the first user 2.

[0040] In some embodiments, in the working fluid circulation path, a fourth temperature measuring point 11 is included between the output end of the hot side of the second heat exchanger 5 and the input end of the second user 3; a flow measuring point 12, a fifth temperature measuring point 13, and a third pressure measuring point 14 are included between the output end of the second user 3 and the input end of the mixing evaporator 1; the control valve assembly includes a second control valve 18 located at the input end of the second user 3. Examples include... Figure 1 As shown, the steam working fluid output from the mixing evaporator 1 passes sequentially through a fourth temperature measuring point 11, a second control valve 18, a flow measuring point 12, a fifth temperature measuring point 13, and a third pressure measuring point 14. The pressure value at the third pressure measuring point 14 can be measured using the measuring assembly; and the temperature values ​​at the fourth temperature measuring point 11 and the fifth temperature measuring point 13 can be measured. Simultaneously, the flow measuring point 12 is used to calculate the mass flow rate of steam entering the first user 2 and the second user 3; while the second control valve 18 is used to control the mass flow rate of steam entering the second user 3.

[0041] In some embodiments, a heat exchange bypass is connected in parallel between the output terminal of the second user 3 and the flow measurement point 12 in the working fluid circulation path; in the heat exchange bypass, an eighth temperature measurement point 20, a sixth temperature measurement point 15 and a seventh temperature measurement point 16 are sequentially provided between the output terminal of the second user 3 and the input terminal of the cold side of the second heat exchanger 5, between the output terminal of the cold side of the second heat exchanger 5 and the input terminal of the cold side of the first heat exchanger 4, and at the output terminal of the cold side of the first heat exchanger 4.

[0042] The heat exchange bypass is connected in parallel between the output of the second user 3 and the flow measurement point 12 in the working fluid circulation path; in other words, the heat exchange bypass is connected in parallel with the working fluid circulation path, and its input is connected to the output of the second user 3, with its output located upstream of the flow measurement point 12. The liquid working fluid output from the second user 3 passes sequentially through the first control valve 17, the eighth temperature measurement point 20, the sixth temperature measurement point 15, and the seventh temperature measurement point 16 at the output of the second user 3, and then through the flow measurement point 12. The first control valve 17 is used to control the mass flow rate of the liquid working fluid entering the heat exchange bypass. The measuring component can measure the temperature values ​​of the eighth temperature measurement point 20, the sixth temperature measurement point 15, and the seventh temperature measurement point 16. In this embodiment, the pressure values ​​of the first pressure measuring point 6, the second pressure measuring point 9, and the third pressure measuring point 14, and the temperature values ​​of the first temperature measuring point 7, the second temperature measuring point 8, the third temperature measuring point 10, the fourth temperature measuring point 11, the fifth temperature measuring point 13, the sixth temperature measuring point 15, the seventh temperature measuring point 16, and the eighth temperature measuring point 20 are measured to calculate the mass flow rate ratio of steam to the first user 2 and the second user 3.

[0043] In some embodiments, a method for operating a steam generation system is provided according to the second aspect of this application, such as... Figure 2 As shown, the steam generation system in any of the above embodiments is operated, including...

[0044] The measuring components are used to obtain the working fluid temperature, pressure and mass flow rate values ​​at multiple measuring points in the steam circulation path, working fluid circulation path and heat exchange bypass;

[0045] The steam flow rates in the steam circulation path and the working fluid circulation path are adjusted using the second control valve 18 and the third control valve 19, so that t2, t4, t6, t7, and t8 conform to the formula:

[0046] To ensure that the mass flow rate of steam at the input and output ends of the first user 2 and the second user 3 are equal;

[0047] Where p1, p2, and p3 are the pressure values ​​(Pa) of the first pressure measuring point 6, the second pressure measuring point 9, and the third pressure measuring point 14, respectively; t1, t2, t3, t4, t5, t6, t7, and t8 are the temperature values ​​(degrees Celsius) of the first temperature measuring point 7, the second temperature measuring point 8, the third temperature measuring point 10, the fourth temperature measuring point 11, the fifth temperature measuring point 13, the sixth temperature measuring point 15, the seventh temperature measuring point 16, and the eighth temperature measuring point 20, respectively; m0 is the mass flow rate (kg / s) of the flow measuring point 12; m u The mass flow rate of the steam at the output end of the first user 2 is kg / s; the thermodynamic specific enthalpy of the working fluid is represented by the function h(t,p).

[0048] in, use The mass flow rate of the gaseous working fluid at the output end of the first user 2 is calculated, and then adjusted by the second control valve 18 and the third control valve 19 to make the mass flow rates of the steam at the input and output ends of the first user 2 and the second user 3 equal.

[0049] In this embodiment, the superheated steam at the output of the first user 2 and the liquid working fluid at the output of the second user 3 exchange heat in the mixing evaporator 1 to generate steam. The steam generated in the mixing evaporator 1 is divided into two parts: one part is slightly cooled by the first heat exchanger 4 and then returns to the inlet of the first user 2 after passing through the third control valve 19; the other part is slightly cooled by the second heat exchanger 5 and then returns to the inlet of the second user 3 after passing through the second control valve 18. The liquid working fluid at the output of the second user 3 is divided into two parts: a large part directly enters the mixing evaporator 1, and a small part first passes through the first control valve 17 and then sequentially enters the second heat exchanger 5 and the first heat exchanger 4 to absorb the heat released by the steam and raise its temperature. The heated liquid working fluid also enters the mixing evaporator 1. To ensure that the mass flow rates of the vaporous working fluid at the input and output of the first user 2 are equal, and that the mass flow rates of the vaporous working fluid at the input and the liquid working fluid at the output of the second user 3 are equal, the system operation also requires the use of the following flow control method:

[0050] The data measured at the first pressure measuring point 6, the second pressure measuring point 9, the third pressure measuring point 14, the first temperature measuring point 7, the second temperature measuring point 8, the third temperature measuring point 10, the fourth temperature measuring point 11, the fifth temperature measuring point 13, the sixth temperature measuring point 15, the seventh temperature measuring point 16, and the eighth temperature measuring point 20 are represented by p1, p2, p3, t1, t2, t3, t4, t5, t6, t7, and t8, respectively. The mass flow rate of the liquid working fluid at the output end of the second user 3 is measured by the flow measuring point 12 and is represented by m0. The mass flow rate of the gaseous working fluid at the output end of the first user 2 is unknown and is represented by m. u The thermodynamic specific enthalpy of the working fluid is expressed using the function h(t,p), m u The ratio to m0 is:

[0051]

[0052]

[0053]

[0054] By adjusting the steam mass flow rates of the two paths in the steam circulation system and the working fluid circulation system using the second control valve 18 and the third control valve 19, t2, t4, t6, t7, and t8 can be made to conform to equation (3). By using equation (1) to calculate the mass flow rate of the vapor working fluid at the output end of the first user 2, the mass flow rates of the working fluid at the input and output ends of the first user 2 and the second user 3 can be made equal.

[0055] It should be noted that in the description of this application, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Furthermore, in the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0056] Any process or method described in the flowchart or otherwise herein can be understood as representing a module, segment, or portion of code comprising one or more executable instructions for implementing a particular logical function or process, and the scope of the preferred embodiments of this application includes additional implementations in which functions may be performed not in the order shown or discussed, including substantially simultaneously or in reverse order depending on the function involved, as will be understood by those skilled in the art to which embodiments of this application pertain.

[0057] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0058] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A steam generating system, characterized in that, include: A mixing evaporator is used to combine superheated steam and liquid working fluid that are simultaneously input at the same pressure to produce steam. A steam circulation system includes a steam circulation path consisting of the hybrid evaporator, the hot side of the first heat exchanger, and a first user; a first pressure measuring point and a first temperature measuring point are included between the output end of the hybrid evaporator and the input end of the hot side of the first heat exchanger; a second temperature measuring point is included between the output end of the hot side of the first heat exchanger and the input end of the first user; a second pressure measuring point and a third temperature measuring point are included between the output end of the first user and the input end of the hybrid evaporator. The working fluid circulation system includes a working fluid circulation loop system and a heat exchange bypass system; wherein the working fluid circulation loop system includes a working fluid circulation path consisting of the mixing evaporator, the hot side of the second heat exchanger, and the second user; a fourth temperature measuring point is included between the output end of the hot side of the second heat exchanger and the input end of the second user; a flow measuring point, a fifth temperature measuring point, and a third pressure measuring point are included between the output end of the second user and the input end of the mixing evaporator; the heat exchange bypass system includes a heat exchange bypass consisting of the output end of the second user, the cold side of the second heat exchanger, and the cold side of the first heat exchanger. In the heat exchange bypass, an eighth temperature measuring point, a sixth temperature measuring point, and a seventh temperature measuring point are sequentially installed between the output terminal of the second user and the input terminal of the cold side of the second heat exchanger, between the output terminal of the cold side of the second heat exchanger and the input terminal of the cold side of the first heat exchanger, and at the output terminal of the cold side of the first heat exchanger; and A measurement and control assembly includes a control valve group and a measurement component; wherein the measurement component is used to measure the working fluid temperature, pressure, and mass flow rate at multiple measurement points in the steam circulation path, the working fluid circulation path, and the heat exchange bypass; the control valve group is used to control the mass flow rate of the working fluid in each path so that t2, t4, t6, t7, and t8 conform to the formula: Where p1, p2, and p3 are the pressure values ​​(Pa) of the first, second, and third pressure measuring points, respectively; t1, t2, t3, t4, t5, t6, t7, and t8 are the temperature values ​​(°C) of the first, second, third, fourth, fifth, sixth, seventh, and eighth temperature measuring points, respectively; the thermodynamic specific enthalpy of the working fluid is represented by the function h(t,p); and the mass flow rate of steam at the input and output ends of the first and second users is made equal.

2. The steam generating system according to claim 1, characterized in that, Measurement points are distributed on the pipelines between the hybrid evaporator, the hot side of the first heat exchanger, and the first user; the control valve group includes a third control valve located at the input end of the first user.

3. The steam generating system according to claim 1 or 2, characterized in that, The control valve assembly includes a second control valve located at the input terminal of the second user.

4. The steam generating system according to claim 3, characterized in that, The heat exchange bypass is connected in parallel between the output terminal of the second user and the flow measurement point in the working fluid circulation path.

5. The steam generating system according to claim 4, characterized in that, The control valve assembly includes a first control valve located at the output end of the second user.

6. A method for operating a steam generation system, characterized in that, Operating the steam generation system according to any one of claims 1-5, including The measuring components are used to obtain the working fluid temperature, pressure and mass flow rate values ​​at multiple measuring points in the steam circulation path, working fluid circulation path and heat exchange bypass; The steam flow rates in the steam circulation path and the working fluid circulation path are adjusted using the second and third control valves to ensure that t2, t4, t6, t7, and t8 conform to the formula: To ensure that the mass flow rate of steam at the input and output terminals of the first and second users are equal; Where p1, p2, and p3 are the pressure values ​​of the first, second, and third pressure measuring points, respectively, in Pa; t1, t2, t3, t4, t5, t6, t7, and t8 are the temperature values ​​of the first, second, third, fourth, fifth, sixth, seventh, and eighth temperature measuring points, respectively, in °C; the thermodynamic specific enthalpy of the working fluid is represented by the function h(t,p).

7. The operating method according to claim 6, characterized in that, in, The mass flow rate of the liquid working fluid at the output terminal of the second user is measured by the flow meter and denoted by m0. The mass flow rate of the vapor working fluid at the output terminal of the first user is unknown and denoted by m0. u The thermodynamic specific enthalpy of the working fluid is expressed using the function h(t,p), m u The ratio to m0 is: ， use The mass flow rate of the vapor working fluid at the output end of the first user is calculated, and adjusted by the second control valve and the third control valve to achieve the same mass flow rate of steam at the input and output ends of the first and second users.

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