A phase modifier plant heating device based on waste heat utilization and a control method thereof

Abstract

The application belongs to the technical field of power engineering and engineering thermophysics, and provides a phase modifier plant heating device based on waste heat utilization and a control method thereof, which comprises a mixing device, a fresh air collecting pipeline arranged at an air inlet end of the mixing device, a phase modifier arranged at an air outlet end of the mixing device, and an exhaust air pipeline arranged at an air outlet end of the phase modifier; an exhaust air outlet is arranged at one end of the exhaust air pipeline, and the other end of the exhaust air pipeline is connected to the air inlet end of the mixing device through an return air collecting pipeline; a fan is arranged in the fresh air collecting pipeline, the exhaust air pipeline, and the return air collecting pipeline; all the fans, the phase modifier, and the mixing device are connected with a controller, and the controller is configured to control the fresh air volume and the return air volume according to the parameters of indoor air and outdoor air in the plant, accurately evaluate the flow and heat of the exhaust air, the return air, and the fresh air of the phase modifier, and has a good heating effect and can efficiently recover the waste heat generated in the operation process of the phase modifier.

Description

Technical Field

[0001] This invention belongs to the field of power engineering and engineering thermophysics, and particularly relates to a heating device and control method for a synchronous condenser plant based on waste heat utilization. Background Technology

[0002] In the field of factory heating, existing technologies mainly include electric heating, gas heating, steam heating and heat pump systems. Each of these heating technologies has its own advantages, but they generally suffer from problems such as high energy consumption, environmental pollution and high cost. Based on this, heating devices based on the utilization of waste heat from condensers have emerged, which can realize the recovery and utilization of waste heat, reduce operating costs, improve energy efficiency, and make a positive contribution to environmental protection.

[0003] Currently, heating devices based on the utilization of waste heat from synchronous condensers cannot efficiently recover the waste heat generated during the operation of the synchronous condensers. These devices mostly rely on fixed heating parameters and lack the ability to dynamically adjust to the actual operating conditions of the plant. This results in uneven heating effects in different seasons and under different load conditions, and even overheating or insufficient heating in some areas. Specifically, during the control process, it is impossible to accurately assess the flow rate and heat of the exhaust, return, and fresh air from the synchronous condenser, leading to poor heating performance. Summary of the Invention

[0004] To address the aforementioned problems, this invention proposes a heating device and control method for a synchronous condenser factory based on waste heat utilization. By controlling the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory, the invention can accurately assess the flow rate and heat of exhaust, return, and fresh air from the synchronous condenser, resulting in a better heating effect and efficient recovery of waste heat generated during the operation of the synchronous condenser.

[0005] To achieve the above objectives, in a first aspect, the present invention provides a heating device for a synchronous condenser factory based on waste heat utilization, employing the following technical solution:

[0006] A heating device for a synchronous condenser factory based on waste heat utilization includes a mixing device, a fresh air collection duct installed at the air inlet of the mixing device, a synchronous condenser installed at the air outlet of the mixing device, and an exhaust duct installed at the air outlet of the synchronous condenser.

[0007] One end of the exhaust duct is provided with an exhaust port, and the other end is connected to the air inlet of the mixing device through a return air collection duct; fans are installed in the fresh air collection duct, the exhaust duct, and the return air collection duct; all fans, synchronous condensers, and the mixing device are connected to a controller, which is configured to control the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory.

[0008] Furthermore, air filtration devices are installed in the end of the exhaust duct near the exhaust port, in the outlet of the return air collection duct, and in the inlet of the fresh air collection duct.

[0009] Furthermore, the air outlet of the mixing device includes an end air outlet and a side air outlet, with the side air outlet facing the air inlet of the condenser.

[0010] To achieve the above objectives, in a second aspect, the present invention also provides a control method for a synchronous condenser factory heating device based on waste heat utilization, employing the following technical solution:

[0011] A control method for a synchronous condenser factory heating device based on waste heat utilization, using the synchronous condenser factory heating device based on waste heat utilization as described in the first aspect, includes: controlling the fresh air volume and return air volume according to the parameters of indoor air and outdoor air in the factory.

[0012] Furthermore, the indoor temperature and relative humidity of the factory are compared with the set temperature and relative humidity. If the indoor temperature is higher than the set temperature, the temperature is lowered; otherwise, the temperature is raised. If the indoor relative humidity is higher than the set relative humidity, the humidity is dehumidified; otherwise, the humidity is increased.

[0013] Furthermore, the required fresh air volume, return air volume, and exhaust air volume for the synchronous condenser plant are calculated, and the fan parameters are adjusted accordingly: The heat load of the building envelope is calculated based on outdoor air parameters; the outlet temperature of the synchronous condenser is calculated based on its heat exchange capacity and air volume, as well as the isobaric specific heat capacity and density at the inlet state point; the specific enthalpy, isobaric specific heat capacity, and density of the outlet air are determined using the isoenthalpy humidification principle; the state point parameters of the outlet air are determined using the isoenthalpy humidification principle; and the fresh air volume, exhaust air volume, and return air volume are calculated using the plant's heat balance equation.

[0014] Calculate the fresh air power and exhaust power based on the fresh air volume, outdoor air specific enthalpy, indoor ambient temperature, outdoor air temperature, heat exchange of the synchronous condenser, and the heat load of the factory building envelope.

[0015] Furthermore, the heat load Q0 of the factory building envelope is:

[0016] Q0=α×U×A×(t n -t wn )

[0017]

[0018] Where Q0 represents the heat load of the factory building envelope; α represents the correction factor for the factory building envelope; U represents the average heat transfer coefficient of the factory building envelope; A represents the area of ​​the factory building envelope; t wn Indicates outdoor air temperature; t nIndicates indoor ambient temperature; α n α represents the heat transfer coefficient of the inner surface of the building envelope; w α represents the heat transfer coefficient of the outer surface of the building envelope; δ represents the thickness of each layer of material in the main section of the building envelope; λ represents the thermal conductivity of each layer of material in the main section of the building envelope; α λ R represents the correction factor for the thermal conductivity of the material. k This indicates the thermal resistance of the air gap in the main cross-section.

[0019] Furthermore, the heat generated by the camera modulator and the airflow of the camera modulator are as follows:

[0020] Q txj =c p2 ×ρ2×V txj ×(t3-t n )

[0021] h3,c p3 ,ρ3=f(t3,P wn ,HR2)

[0022] Among them, Q txj This indicates the heat generated by the camera; c p2 ρ and ρ2 represent the isobaric specific heat capacity and density at the inlet of the condenser, respectively; V txj t3 represents the airflow of the camera regulator; t3 represents the outlet temperature of the camera regulator; t n h3 is the indoor ambient temperature; h3 is the specific enthalpy at the outlet of the synchronous condenser; c p3 ρ3 is the specific heat capacity at constant pressure at the outlet of the condenser; P is the density at the outlet of the condenser. wn RH2 represents indoor ambient pressure; RH2 represents indoor relative humidity.

[0023] Furthermore, assuming the fresh air volume and exhaust air volume are the same, the fresh air volume, exhaust air volume, and return air volume are calculated using the plant's heat balance equation:

[0024] Q txj =Q0+Q new +Q pai

[0025] Q new =ρ1×V new ×(h3-h1)

[0026] V txj =V pai +V hui

[0027] V new =V pai

[0028] Among them, Q txj Q represents the heat generated by the synchronous condenser; Q0 is the heat load of the factory building; Qnew For fresh air heat load; Q pai The heat load leaving the factory building; ρ1 represents the outdoor air density; V new Indicates fresh air volume; h3 is the specific enthalpy of the synchronous condenser outlet; h1 is the specific enthalpy of outdoor air; V txj Indicates the airflow at the camera outlet; V pai To adjust the exhaust air at the camera outlet; V hui Adjust the return air at the camera outlet.

[0029] Furthermore, the fresh air power and exhaust air power are as follows:

[0030] Q new =m new ×c p1 ×(t n -t wn )

[0031] Q pai =Q txj -Q0-Q new

[0032] Where, m new c is the fresh air volume; p1 Specific enthalpy of outdoor air; t n Indoor ambient temperature; t wn Outdoor air temperature; Q txj Q is the heat exchange of the camera; Q0 is the heat load of the factory building envelope; Q new For fresh air supply power; Q pai This refers to the exhaust power.

[0033] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0034] 1. In this invention, an exhaust vent is provided at one end of the exhaust duct, and the other end is connected to the air inlet of the mixing device through a return air collection duct; fans are installed in the fresh air collection duct, the exhaust duct, and the return air collection duct; all fans, synchronous condensers, and mixing devices are connected to a controller, which is configured to control the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory, accurately assess the flow rate and heat of exhaust, return, and fresh air of the synchronous condenser, provide good heating effect, and efficiently recover the waste heat generated during the operation of the synchronous condenser.

[0035] 2. In this invention, the indoor temperature and relative humidity of the factory are compared with the set temperature and relative humidity. If the indoor temperature is higher than the set temperature, the temperature is lowered; otherwise, the temperature is raised. If the indoor relative humidity is higher than the set relative humidity, dehumidification is performed; otherwise, humidification is performed. Based on this, the fresh air volume and return air volume are controlled according to the parameters of the indoor and outdoor air in the factory. The dynamic adjustment capability for the actual operating conditions of the factory enables the factory to achieve uniform heating effect under different seasons and load conditions. Attached Figure Description

[0036] The accompanying drawings, which form part of this embodiment, are used to provide a further understanding of this embodiment. The illustrative embodiments and their descriptions are used to explain this embodiment and do not constitute an improper limitation of this embodiment.

[0037] Figure 1 This is a schematic diagram of the mixing of fresh air, return air and exhaust air in the system of Embodiment 1 of the present invention;

[0038] Figure 2 This is a flowchart of the system air volume calculation in Embodiment 1 of the present invention;

[0039] Figure 3 The changes in fresh air load, exhaust air load, and air volume with indoor temperature in Embodiment 1 of the present invention;

[0040] Figure 4 This describes the PID control process of the axial flow fan in Embodiment 1 of the present invention.

[0041] Figure 5 This is a flowchart of the dynamic control intelligent waste heat utilization heating system of Embodiment 1 of the present invention. Detailed Implementation

[0042] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0043] It should be noted that the following detailed descriptions are exemplary and intended to provide further explanation of this application. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0044] Example 1:

[0045] With the continuous development of industrial production, especially in the power and electrical equipment manufacturing sector, synchronous condensers, as important electrical equipment, generate a large amount of waste heat during operation. If this waste heat is not utilized, it will be directly released into the environment, not only wasting resources but also potentially negatively impacting the temperature and humidity within the factory. Therefore, effectively recovering and utilizing the waste heat from synchronous condensers has become a key technology for improving energy efficiency and the factory environment. Traditional heating systems often use electric heating or fuel combustion for indoor heating, which is not only energy-intensive but also causes environmental pollution. The heat generated by synchronous condensers, however, is characterized by stable temperature and sufficient heat, providing a new solution for factory heating.

[0046] Specifically, in the field of factory heating, existing technologies mainly include electric heating, gas heating, steam heating, and heat pump systems. Electric heating systems quickly heat air or water directly using electricity, and are simple to operate, but their high energy consumption and expensive electricity prices significantly increase operating costs and may put pressure on the environment. Gas heating systems provide heat by burning natural gas; although they are highly energy efficient, their reliance on fossil fuels leads to greenhouse gas emissions, and they face challenges from fluctuating gas prices and unstable supply. Steam heating systems use boilers to heat water into steam, providing stable heat; however, their construction and maintenance costs are high, their energy efficiency is relatively low, and they suffer from heat loss. Heat pump heating systems extract heat from low-temperature environments to achieve high-efficiency heating, but their efficiency decreases at low temperatures, they require large initial investments, and they demand high levels of installation and maintenance. In summary, although existing heating technologies each have their advantages, they generally suffer from high energy consumption, environmental pollution, and high costs, necessitating the development of more efficient and environmentally friendly heating solutions. Heating devices based on the utilization of waste heat from synchronous condensers are an effective solution to these challenges. They enable the recovery and utilization of waste heat, reduce operating costs, improve energy efficiency, and make a positive contribution to environmental protection.

[0047] However, in modern industrial plant heating systems, effective airflow and thermal management are key to achieving energy efficiency and a comfortable environment. In existing plant heating systems, the indoor heat load is entirely provided by fresh air, while the waste heat discharged by the synchronous condenser is mostly directly discharged into the atmosphere, resulting in extremely low waste heat utilization efficiency and failing to fully utilize the potential of industrial equipment. In addition, traditional heating systems rely heavily on fixed heating parameters and lack the ability to dynamically adjust to the actual operating conditions of the plant. This deficiency leads to uneven heating effects in different seasons and under different load conditions, and even overheating or underheating in some areas.

[0048] To solve at least one of the above problems, such as Figure 1As shown, this embodiment provides a waste heat utilization-based synchronous condenser factory heating device. It aims to establish a scientific calculation process to accurately assess the exhaust, return, and fresh air flow and heat of the synchronous condenser, thereby optimizing the heating effect. First, by monitoring the synchronous condenser's operating status in real time, its airflow and waste heat are obtained. Simultaneously, considering the factory's heat load requirements, external ambient temperature, and humidity, the exhaust, return, and fresh air volumes are calculated in real time. This embodiment also addresses the flexibility and adaptability issues of heating systems. Traditional heating systems often struggle to adjust to the actual needs of the factory, leading to energy waste. The waste heat utilization-based heating device combines intelligent control technology to monitor parameters such as temperature and humidity within the factory in real time, intelligently adjusting the heating mode to achieve dynamic temperature control and ensure the factory remains in a comfortable environment. The factory heating system of this embodiment includes a mixing device, a fresh air collection duct installed at the air inlet of the mixing device, a synchronous condenser installed at the air outlet of the mixing device, and an exhaust duct installed at the air outlet of the synchronous condenser. One end of the exhaust duct has an exhaust port, and the other end is connected to the air inlet of the mixing device via a return air collection duct. Air filters are installed in the end of the exhaust duct near the exhaust port, in the air outlet of the return air collection duct, and in the air inlet of the fresh air collection duct. The air outlet of the mixing device includes an end outlet and a side outlet, with the side outlet facing the air inlet of the synchronous condenser. It is understood that fans are installed in the fresh air collection duct, the exhaust duct, and the return air collection duct, and all fans, the synchronous condenser, and the mixing device are connected to a controller.

[0049] The hot air discharged from the synchronous condenser is divided into two parts for processing. One part of the hot air is directly discharged outdoors through the exhaust duct, while the other part is mixed with fresh air introduced from the outside through a mixing device, heating the cold outdoor air to the set comfortable indoor temperature. During this process, after the preheated fresh air enters the factory, a portion is used to maintain the required indoor temperature and humidity to ensure a comfortable working environment; the other part of the hot air continues to be further heated by the synchronous condenser, forming a circulation system. This design not only improves energy efficiency but also ensures the stability of the indoor environment. To maintain pressure balance between indoors and outdoors, the indoor fresh air volume is consistent with the air volume exhausted outdoors. The airflow design in this embodiment ensures stable air pressure inside the factory, helps optimize air quality, and prevents airflow obstruction or temperature fluctuations caused by pressure changes.

[0050] Calculating the fresh air volume, return air volume, and exhaust air volume is crucial for ensuring the efficient operation of a factory heating system. Accurate air volume calculations maintain indoor air quality, prevent overheating or overcooling, improve employee comfort, and help achieve optimal energy utilization, reducing unnecessary energy waste. Therefore, this embodiment, based on the factory heating system, also provides a method for calculating and controlling the air volume of a synchronous condenser factory waste heat recovery system. This method can be implemented through a controller, thereby precisely controlling the fresh air volume and return air volume based on indoor and outdoor air parameters. The air volume calculation process for the factory heating system is as follows: Figure 2 As shown, the optional specific calculation steps are as follows:

[0051] S1. Optionally, based on known outdoor air parameters of the factory building, such as temperature, pressure, and relative humidity, as well as the geometric parameters of the factory building and the heat transfer coefficient of the factory building envelope, calculate the heat load Q0 of the factory building envelope:

[0052] Q0=α×U×A×(t n -t wn )

[0053] Where Q0 represents the heat load of the factory building envelope, in W; α represents the correction factor for the factory building envelope; and U represents the average heat transfer coefficient of the factory building envelope, in W / (m²). 2 ℃); A represents the area of ​​the factory building envelope, m 2 ;t wn Outdoor air temperature, ℃; t n This indicates the indoor ambient temperature, expressed in °C. Temperature, pressure, relative humidity, and other parameters can be collected using temperature sensors, pressure sensors, humidity sensors, and other sensors.

[0054] Optionally, the average heat transfer coefficient U of the plant building envelope is:

[0055]

[0056] Where U represents the average heat transfer coefficient of the building envelope, W / (m²). 2 ℃); α n This represents the heat transfer coefficient of the inner surface of the factory building envelope, in W / (m²). 2 ℃); α w This represents the heat transfer coefficient of the outer surface of the factory building envelope, in W / (m²). 2 ℃); δ represents the thickness of each layer of material in the main section of the factory building envelope, in meters; λ represents the thermal conductivity of each layer of material in the main section of the factory building envelope, in W / (m℃); α λ R represents the correction factor for the thermal conductivity of the material. k The thermal resistance of the air gap in the main cross-section, m 2 ℃ / W.

[0057] S2, Optional, based on the set indoor ambient temperature t n Pressure P wn and moisture content HR n The parameters of the indoor air state point, such as specific enthalpy h2 and specific heat capacity at constant pressure c, can be retrieved through the humid air subroutine in Cool Prop 6.6.0. p2 Density ρ2 and relative humidity RH2, etc.

[0058] h2,c p2 ,ρ2,RH2=f(t n ,P wn HR n )

[0059] S3, subsequently, optionally, based on the heat exchange rate Q of the camera. txj Air volume V txj And the constant pressure specific heat capacity c at the camera inlet state point p2 Given density ρ2, calculate the outlet temperature t3 of the synchronous condenser; using the principle of isenthalpic humidification, determine the state point parameters of the outlet air of the synchronous condenser, such as specific enthalpy h3 and specific heat capacity at constant pressure c. p3 And density ρ3, etc.:

[0060] Q txj =c p2 ×ρ2×V txj ×(t3-t n )

[0061] h3,c p3 ,ρ3=f(t3,P wn ,HR2)

[0062] Among them, Q txj The heat generated by the camera is expressed in W and V. txj This indicates the camera's airflow, in meters. 3 / h;c p2 ρ2 represents the isobaric specific heat capacity at the inlet of the condenser, J / (kg K), and density, kg / m³, respectively. 3 .

[0063] S4. Based on the indoor and outdoor air pressure balance, the fresh air volume V new and exhaust volume V pai Similarly, the fresh air volume, exhaust air volume, and return air volume V are calculated using the plant's heat balance equation. hui The heat generated by the camera will partially heat the outdoor fresh air to the preset temperature Q. new Part of it is used to maintain the heat load Q0 of the factory building envelope, and part is directly discharged into the outdoor atmosphere Q. pai :

[0064] Q txj=Q0+Q new +Q pai

[0065] Q new =ρ1×V new ×(h3-h1)

[0066] V txj =V pai +V hui

[0067] V new =V pai

[0068] Among them, Q new Q0 represents the fresh air heat load, W; Q0 represents the factory heat load, W; Q pai The heat load leaving the factory building is represented by W; ρ1 represents the outdoor air density, kg / m³. 3 V new Indicates fresh air volume, m 3 / h;V txj This indicates the air volume at the outlet of the condenser, which is mainly divided into two parts: one part is used as exhaust air (V). pai One part is discharged into the outdoor atmosphere; the other part serves as return air. hui It mixes with the indoor fresh air.

[0069] Next, determine the fresh air power Q. new And exhaust power Q pai The specific calculation is as follows:

[0070] Q new =m new ×c p1 ×(t n -t wn )

[0071] Q pai =Q txj -Q0-Q new

[0072] Through steps S1 to S4, the heating demand of the factory can be scientifically assessed and precisely controlled, laying the foundation for improving energy efficiency and environmental comfort.

[0073] To further illustrate the control method in this embodiment, the outdoor design parameters for winter in a certain location and the architectural design and construction drawings of a factory building were selected. The fresh air volume, return air volume, and exhaust air volume for waste heat recovery in the factory building were calculated to verify the rationality and feasibility of the proposed calculation and control method. The design parameters and heating parameters are shown in Table 1.

[0074] Table 1. Outdoor design parameters and heating parameters for a certain area in winter.

[0075]

[0076] like Figure 3 As shown, with a condenser heat exchange of 680kW and an outdoor air temperature of -16.6℃, the fresh air volume and exhaust air volume gradually decrease as the indoor air temperature increases. This indicates that as the indoor and outdoor temperature difference gradually increases, the heat load of the fresh air gradually increases. In order to maintain a constant indoor temperature, the required return air volume gradually increases. Therefore, the fresh air volume and exhaust air volume gradually decrease, and the return air load gradually decreases.

[0077] To achieve control over the heating system, this embodiment also provides a dynamically adjustable and intelligent waste heat utilization heating system. Combined with intelligent control technology, it aims to achieve efficient adjustment and dynamic temperature control of the heating system by monitoring environmental parameters within the factory in real time. The system collects indoor temperature, humidity, and other data through sensors and compares them with set comfort standards. It then uses intelligent algorithms to automatically adjust the heating mode to ensure that the factory is always maintained under optimal environmental conditions. Figure 5 The diagram shows the process of a dynamically controlled intelligent waste heat utilization heating system, and its control implementation is as follows:

[0078] System initialization and parameter setting: Users set the target indoor temperature and humidity through the interface. The system records and stores the set values ​​as the basis for subsequent monitoring and adjustment.

[0079] Data acquisition and real-time monitoring: Indoor and outdoor temperature and humidity sensors are installed to monitor the indoor and outdoor environment in real time. The sensors collect indoor and outdoor temperature and humidity data at regular intervals and transmit them to the central control unit.

[0080] Central control unit data processing: The central control unit will process the indoor temperature t collected in real time. n and relative humidity (RH) n With the set temperature t set and relative humidity (RH) set Compare and determine the current state of the factory: If t n >t set If t n <t set Then the temperature needs to be increased; if RH in >RH set If the RH is high, then dehumidification is required; if the RH is low... in <RH set If so, humidification is needed; afterwards, according to Figure 2 The calculation process shown calculates the required fresh air volume, return air volume, and exhaust air volume for the synchronous condenser plant based on input parameters (such as real-time indoor temperature and humidity, and set temperature and humidity), thereby adjusting the fan parameters to meet the plant's set requirements.

[0081] Fan parameter adjustment: A control signal is calculated using PID control. Based on this signal, the fan speed is adjusted, and then the airflow is adjusted according to the speed. This process is repeated to gradually bring the indoor temperature and humidity to the set values ​​and maintain stability. The control process is as follows: Figure 5 As shown. The specific adjustment process is as follows:

[0082] Data acquisition and status judgment: The central control unit collects indoor temperature and humidity data in real time, compares it with the set value, and calculates the error e(t), which is the difference between the set value and the actual value;

[0083] PID controller calculation: The PID controller calculates the control signal u(t) based on the error. The PID control formula is as follows:

[0084]

[0085] Among them, K p Represents proportional gain; K i K represents the integral gain; d The differential gain is represented by e(t); the current error is represented by e(t). It is the integral of the error, representing the accumulation of the error; It is the differential of the error, representing the rate at which the error changes.

[0086] Dynamically adjust the fan speed: Adjust the fan speed v(t) according to the control signal u(t):

[0087] v(t) = v base +u(t)

[0088] Among them, v base The value represents the basic speed of the fan; u(t) represents the adjustment calculated by the PID controller.

[0089] Adjusting the air volume: Changes in fan speed directly affect the air volume Q(t), and the air volume is approximately proportional to the speed.

[0090] Q(t)=k×v(t)

[0091] Where k represents the ratio constant between rotational speed and air volume; Q(t) represents the air volume of the fan.

[0092] Real-time feedback and adjustment: After the fan speed is adjusted, the system will collect indoor temperature and humidity data again to form new feedback and perform PID control in a loop until the set deviation is reached.

[0093] Adaptive Learning and Optimization: During system operation, a large amount of operational data is continuously collected, including airflow, indoor and outdoor temperature and humidity, etc. An adaptive learning algorithm is used to establish a functional relationship model between airflow and indoor and outdoor temperature and humidity. The specific process includes data preparation, model selection, defining the loss function, and applying gradient descent to update parameters, ultimately obtaining a model that can accurately predict airflow. Based on the model predictions, the fan's operating parameters are optimized in real time to improve the system's response speed and stability. The specific implementation steps are as follows:

[0094] Data preparation: Collect a series of historical data, including indoor temperature (t). n Indoor humidity (RH) n Outdoor temperature t wn Outdoor humidity RH wn and the required air volume Q;

[0095] Model Selection: Assuming that the air volume Q can be represented by a linear combination of indoor and outdoor temperature and humidity, the selected linear model is as follows:

[0096] Q = θ0 + θ1t n +θ2RH n +θ3t wn +θ4RH wn

[0097] Loss function: To evaluate the predictive performance of the model, a loss function is defined:

[0098]

[0099] Where m represents the number of samples; Q represents the air volume predicted by the model for the i-th sample; (i) This represents the actual air volume of the i-th sample.

[0100] Gradient descent algorithm: The model parameters θ are continuously adjusted using the gradient descent algorithm to minimize the loss function.

[0101]

[0102] Where α represents the learning rate, controlling the step size; gradient The calculation formula is:

[0103]

[0104] Model Update: In each iteration, the model is updated using new parameters θ until the loss function converges to a small value or the preset maximum number of iterations is reached. The final model parameters θ represent the relationship between airflow and indoor / outdoor temperature and humidity.

[0105] Feedback and Adjustment: The system continuously monitors changes in indoor and outdoor temperature and humidity to ensure stable operation within the set range. If the indoor temperature and humidity do not meet the set requirements, the fan parameters are recalculated and the operating strategy is adjusted.

[0106] It is worth noting that this invention combines system control with artificial intelligence, achieving proactive control of operating parameters through adaptive learning and optimization methods. This approach not only improves control accuracy and adaptability, optimizes energy utilization, enhances system stability, and reduces maintenance costs, but also improves user experience and promotes the progress of intelligent management, demonstrating significant economic and environmental benefits.

[0107] Example 2:

[0108] This embodiment provides a control method for a synchronous condenser factory heating device based on waste heat utilization. It uses the synchronous condenser factory heating device based on waste heat utilization as described in Embodiment 1, including: controlling the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory.

[0109] Optionally, the indoor temperature and relative humidity of the factory can be compared with the set temperature and relative humidity. If the indoor temperature is higher than the set temperature, the temperature will be lowered; otherwise, the temperature will be raised. If the indoor relative humidity is higher than the set relative humidity, the humidity will be dehumidified; otherwise, the humidity will be increased.

[0110] Calculate the required fresh air volume, return air volume, and exhaust air volume for the synchronous condenser plant, and adjust the fan parameters accordingly: Calculate the heat load of the building envelope based on outdoor air parameters; calculate the outlet temperature of the synchronous condenser based on its heat exchange and air volume, as well as the isobaric specific heat capacity and density at the inlet state point; determine the specific enthalpy, isobaric specific heat capacity, and density of the outlet air using the isoenthalpy humidification principle; determine the state point parameters of the outlet air using the isoenthalpy humidification principle; calculate the fresh air volume, exhaust air volume, and return air volume using the plant's heat balance equation.

[0111] Calculate the fresh air power and exhaust power based on the fresh air volume, outdoor air specific enthalpy, indoor ambient temperature, outdoor air temperature, heat exchange of the synchronous condenser, and the heat load of the factory building envelope.

[0112] Optionally, the heat load Q0 of the factory building envelope is:

[0113] Q0=α×U×A×(t n -t wn )

[0114]

[0115] Where Q0 represents the heat load of the factory building envelope; α represents the correction factor for the factory building envelope; U represents the average heat transfer coefficient of the factory building envelope; A represents the area of ​​the factory building envelope; twn Indicates outdoor air temperature; t n Indicates indoor ambient temperature; α n α represents the heat transfer coefficient of the inner surface of the building envelope; w α represents the heat transfer coefficient of the outer surface of the building envelope; δ represents the thickness of each layer of material in the main section of the building envelope; λ represents the thermal conductivity of each layer of material in the main section of the building envelope; α λ R represents the correction factor for the thermal conductivity of the material. k This indicates the thermal resistance of the air gap in the main cross-section.

[0116] Optionally, the heat generated by the camera and the airflow of the camera are:

[0117] Q txj =c p2 ×ρ2×V txj ×(t3-t n )

[0118] h3,c p3 ,ρ3=f(t3,P wn ,HR2)

[0119] Among them, Q txj This indicates the heat generated by the camera; c p2 ρ and ρ2 represent the isobaric specific heat capacity and density at the inlet of the condenser, respectively; V txj t3 represents the airflow of the camera regulator; t3 represents the outlet temperature of the camera regulator; t n h3 is the indoor ambient temperature; h3 is the specific enthalpy at the outlet of the synchronous condenser; c p3 ρ3 is the specific heat capacity at constant pressure at the outlet of the condenser; P is the density at the outlet of the condenser. wn RH2 represents indoor ambient pressure; RH2 represents indoor relative humidity.

[0120] Optionally, the fresh air volume and exhaust air volume are the same, and the fresh air volume, exhaust air volume, and return air volume are calculated using the plant's heat balance equation:

[0121] Q txj =Q0+Q new +Q pai

[0122] Q new =ρ1×V new ×(h3-h1)

[0123] V txj =V pai +V hui

[0124] V new =V pai

[0125] Among them, Qtxj Q represents the heat generated by the synchronous condenser; Q0 is the heat load of the factory building; Q new For fresh air heat load; Q pai The heat load leaving the factory building; ρ1 represents the outdoor air density; V new Indicates fresh air volume; h3 is the specific enthalpy of the synchronous condenser outlet; h1 is the specific enthalpy of outdoor air; V txj Indicates the airflow at the camera outlet; V pai To adjust the exhaust air at the camera outlet; V hui Adjust the return air at the camera outlet.

[0126] Optional, the fresh air power and exhaust air power are:

[0127] Q new =m new ×c p1 ×(t n -t wn )

[0128] Q pai =Q txj -Q0-Q new

[0129] Where, m new c is the fresh air volume; p1 Specific enthalpy of outdoor air; t n Indoor ambient temperature; t wn Outdoor air temperature; Q txj Q is the heat exchange of the camera; Q0 is the heat load of the factory building envelope; Q new For fresh air supply power; Q pai This refers to the exhaust power.

[0130] The above description is merely a preferred embodiment of this practice and is not intended to limit the scope of this practice. Various modifications and variations can be made to this practice by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this practice should be included within the protection scope of this practice.

Claims

1. A heating device for a synchronous condenser factory based on waste heat utilization, characterized in that, It includes a mixing device, a fresh air collection duct installed at the air inlet of the mixing device, a synchronous condenser installed at the air outlet of the mixing device, and an exhaust duct installed at the air outlet of the synchronous condenser. One end of the exhaust duct is provided with an exhaust port, and the other end is connected to the air inlet of the mixing device through a return air collection duct; fans are installed in the fresh air collection duct, the exhaust duct, and the return air collection duct; all fans, synchronous condensers, and the mixing device are connected to a controller, which is configured to control the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory. Calculate the required fresh air volume, return air volume, and exhaust air volume for the synchronous condenser plant, and adjust the fan parameters accordingly. Calculate the heat load of the building envelope based on outdoor air parameters. Calculate the outlet temperature of the synchronous condenser based on its heat exchange capacity and air volume, as well as its constant pressure specific heat capacity and density at the inlet point. Using the principle of isenthalpic humidification, the specific enthalpy, specific heat capacity at constant pressure, and density of the air at the outlet of the synchronous condenser are determined; using the principle of isenthalpic humidification, the state point parameters of the air at the outlet of the synchronous condenser are determined; and the fresh air volume, exhaust air volume, and return air volume are calculated using the plant heat balance equation. Calculate the fresh air power and exhaust power based on the fresh air volume, outdoor air specific enthalpy, indoor ambient temperature, outdoor air temperature, heat exchange of the synchronous condenser, and the heat load of the factory building envelope.

2. The synchronous condenser factory heating device based on waste heat utilization as described in claim 1, characterized in that, An air filtration device is installed in the end of the exhaust duct near the exhaust port, in the outlet of the return air collection duct, and in the inlet of the fresh air collection duct.

3. The synchronous condenser factory heating device based on waste heat utilization as described in claim 1, characterized in that, The air outlet of the mixing device includes an end air outlet and a side air outlet, with the side air outlet facing the air inlet of the condenser.

4. A control method for a synchronous condenser factory heating system based on waste heat utilization, characterized in that, The heating device for a synchronous condenser factory building based on waste heat utilization as described in any one of claims 1-3 includes: controlling the fresh air volume and return air volume according to the parameters of indoor and outdoor air in the factory building.

5. The control method for a synchronous condenser factory heating system based on waste heat utilization as described in claim 4, characterized in that, The indoor temperature and relative humidity of the factory are compared with the set temperature and relative humidity. If the indoor temperature is higher than the set temperature, the temperature is lowered; otherwise, the temperature is raised. If the indoor relative humidity is higher than the set relative humidity, the humidity is dehumidified; otherwise, the humidity is increased.

6. The control method for a synchronous condenser factory heating device based on waste heat utilization as described in claim 5, characterized in that, Calculate the required fresh air volume, return air volume, and exhaust air volume for the synchronous condenser plant, and adjust the fan parameters accordingly. Calculate the heat load of the building envelope based on outdoor air parameters. Calculate the outlet temperature of the synchronous condenser based on its heat exchange capacity and air volume, as well as its constant pressure specific heat capacity and density at the inlet point. Using the principle of isenthalpic humidification, the specific enthalpy, specific heat capacity at constant pressure, and density of the air at the outlet of the synchronous condenser are determined; using the principle of isenthalpic humidification, the state point parameters of the air at the outlet of the synchronous condenser are determined; and the fresh air volume, exhaust air volume, and return air volume are calculated using the plant heat balance equation. Calculate the fresh air power and exhaust power based on the fresh air volume, outdoor air specific enthalpy, indoor ambient temperature, outdoor air temperature, heat exchange of the synchronous condenser, and the heat load of the factory building envelope.

7. The control method for a synchronous condenser factory heating system based on waste heat utilization as described in claim 6, characterized in that, Factory building envelope heat load Q 0 is: in, Q 0 represents the heat load of the factory building envelope; α Indicates the correction factor for the factory building envelope; U This represents the average heat transfer coefficient of the factory building envelope; A Indicates the area of ​​the factory building's enclosure structure; t wn Indicates outdoor air temperature; t n Indicates indoor ambient temperature; α n Indicates the heat transfer coefficient of the inner surface of the factory building envelope; α w Indicates the heat transfer coefficient of the outer surface of the building envelope; δ This indicates the thickness of each layer of material in the main section of the factory building's enclosure structure; λ This indicates the thermal conductivity of each layer of material in the main section of the factory building envelope; α λ A correction factor representing the thermal conductivity of a material; R k This indicates the thermal resistance of the air gap in the main cross-section.

8. The control method for a synchronous condenser factory heating system based on waste heat utilization as described in claim 6, characterized in that, The heat generated by the camera modulator and the airflow of the camera modulator are: in, Q txj This indicates the heat generated by the camera. c p2 and ρ 2 represents the isobaric specific heat capacity and density at the inlet of the synchronous condenser, respectively; V txj Indicates the airflow rate of the camera; t 3 is for adjusting the camera outlet temperature; t n Indoor ambient temperature; h 3 represents the specific enthalpy at the output of the camera; c p3 To adjust the specific heat capacity at constant pressure at the camera outlet; ρ 3 represents the output density of the camera; P wn For indoor environmental pressure; RH 2 represents the indoor relative humidity.

9. The control method for a synchronous condenser factory heating system based on waste heat utilization as described in claim 6, characterized in that, The fresh air volume and exhaust air volume are the same. The fresh air volume, exhaust air volume, and return air volume are calculated using the plant's heat balance equation: in, Q txj This indicates the heat generated by the camera. Q 0 represents the factory's heat load; Q new For fresh air heat load; Q pai The heat load leaving the factory building; ρ 1 represents outdoor air density; V new Indicates the fresh air volume; h 3. Adjust the specific enthalpy of the camera outlet; h 1. Specific enthalpy of outdoor air; V txj This indicates the airflow at the camera's outlet. V pai To adjust the exhaust air at the camera outlet; V hui Adjust the return air at the camera outlet.

10. The control method for a synchronous condenser factory heating device based on waste heat utilization as described in claim 6, characterized in that, The fresh air power and exhaust air power are: in, For fresh air volume; Specific enthalpy of outdoor air; Indoor ambient temperature; Outdoor air temperature; For adjusting the heat exchange of the camera; The heat load of the factory building envelope; For fresh air supply power; Q pai This refers to the exhaust power.

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