A ground source heat pump coupled fresh air dehumidification system and method

Abstract

The application belongs to the technical field of ground source heat pumps, and particularly relates to a ground source heat pump coupled fresh air dehumidification system and method, wherein the ground source heat pump coupled fresh air dehumidification system comprises a sensing module: used for collecting air side and water side operation parameters, including a water inlet temperature sensor arranged on a cold water inlet pipe section of a fresh air dehumidifier, used for obtaining real-time chilled water inlet temperature; a face wind speed meter arranged on a windward side of a surface air cooler, used for obtaining real-time face wind speed; a condensate water flow meter arranged on a water collecting pan drainage vertical pipe, used for obtaining instantaneous drainage flow rate; an inlet air temperature and humidity and dew point sensor arranged on a straight air inlet section, used for obtaining inlet air dry bulb temperature, inlet air relative humidity and inlet air dew point temperature; and an outlet air temperature and humidity sensor arranged on an outlet air section; the ground source heat pump coupled fresh air dehumidification system realizes a leap from passive constant parameter control to active thermodynamic optimization, has self-locking degradation capability in the case of data distortion, and greatly improves dehumidification energy efficiency and pipe network safety.

Description

Technical Field

[0001] This invention belongs to the field of ground source heat pump technology, specifically a ground source heat pump coupled with a fresh air dehumidification system and method. Background Technology

[0002] Ground source heat pump coupled fresh air dehumidification systems are widely used in air environment control in high-energy-efficiency buildings. Typically, these systems respond to changes in indoor and outdoor temperature and humidity loads by adjusting the flow rate of chilled water into the surface cooler.

[0003] However, existing control logic has revealed significant limitations in practical engineering applications. First, traditional control methods mostly rely on simple PID feedback regulation of indoor return air temperature and humidity, without deeply analyzing the heat transfer limits of airflow and water flow at the heat exchange boundary layer, nor assessing the true proportion of cooling capacity converted into pure dehumidification latent heat. This leads to the system blindly driving the water valve based solely on surface temperature and humidity deviations when facing drastically fluctuating fresh air loads, which can easily cause sensible heat and cooling capacity to overflow while latent heat dehumidification is insufficient, resulting in excessive ineffective circulation of cold water and huge waste of pumping energy.

[0004] Secondly, the engineering site environment is complex. Condensate often escapes due to high wind speeds or is blocked by impurities in the drainage pipes. In addition, temperature and humidity sensors are prone to zero-point drift. Existing systems generally adopt an "unconditional trust" execution mechanism for the data from the underlying sensors, lacking the ability to self-diagnose the conservation of physical processes. Once the data source is distorted, the control logic will continuously send erroneous deviation compensation commands to the actuator, causing the regulating valve to oscillate and diverge over a wide range, and even leading to the collapse of the hydraulic network control.

[0005] Therefore, the present invention provides a ground source heat pump coupled fresh air dehumidification system and method. Summary of the Invention

[0006] In order to overcome the shortcomings of the prior art, at least one technical problem raised in the background art is solved.

[0007] The technical solution adopted by this invention to solve its technical problem is: a ground source heat pump coupled fresh air dehumidification system according to this invention, comprising:

[0008] Sensing Module: Used to collect air-side and water-side operating parameters, including an inlet water temperature sensor installed in the chilled water inlet pipe section of the fresh air dehumidifier to obtain the real-time chilled water inlet temperature; a frontal anemometer installed on the windward side of the surface cooler to obtain the real-time frontal wind speed; a condensate flow meter installed in the drain riser of the water tray to obtain the instantaneous drainage flow rate; inlet air temperature, humidity, and dew point sensors installed in the intake section to obtain the inlet dry-bulb temperature, inlet relative humidity, and inlet dew point temperature; outlet air temperature and humidity sensors installed in the supply section to obtain the outlet dry-bulb temperature and outlet relative humidity; a surface temperature sensor installed on the coil surface to obtain the coil surface dry-bulb temperature; and a chilled water flow meter installed in the return water section to obtain the real-time chilled water volumetric flow rate.

[0009] Control module: interconnected with the sensing module via a communication bus, internally encapsulating a cold air coupling model, a latent heat conversion model, a supply-demand two-dimensional mapping model, a dehumidification reliability model, and a chilled water real-time flow optimization model; the control module is configured to generate source-load synergy and dehumidification reliability based on the acquired operating parameters, and output the target chilled water volume flow rate command;

[0010] Flow actuator: includes an electric regulating valve connected in series in the return water section, the pipeline of which is connected to the manifold of the ground source heat pump host to form a cold water circulation loop; the electric regulating valve is configured to receive the target chilled water volume flow command and perform the corresponding valve core displacement action.

[0011] A dehumidification method for a ground source heat pump coupled with fresh air, applied to the aforementioned ground source heat pump coupled with fresh air dehumidification system, includes the following steps:

[0012] S1: Real-time acquisition of air and water side operating parameters via the sensing module and transmission to the control module;

[0013] S2: When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, it activates the internal cold air coupling model and latent heat conversion model to calculate and obtain the cold air coupling degree and latent heat conversion effectiveness.

[0014] S3: The control module activates the internal supply and demand two-dimensional mapping model and dehumidification reliability model to calculate and obtain the external load demand, internal operating effectiveness, and dehumidification reliability.

[0015] S4: The control module activates the internal real-time chilled water flow optimization model, extracts the external load demand, internal operating efficiency and dehumidification reliability, and calculates and generates the target chilled water volume flow command.

[0016] S5: The electric regulating valve receives the target chilled water volume flow command, executes the corresponding valve core displacement action, and adjusts the flow area of ​​the chilled water entering the surface cooler.

[0017] The beneficial effects of this invention are as follows:

[0018] 1. This invention sets up a cold air coupling model and a latent heat conversion model, and quantifies the heat transfer limit of the heat exchange boundary layer of the surface cooler and the latent heat dehumidification ratio based on real-time operating parameters. When the cold air coupling degree or latent heat conversion efficiency drops to the lower limit, the valve position is actively restricted, avoiding the problem of insufficient latent heat dehumidification due to the overflow of sensible heat in traditional control, and effectively suppressing ineffective cold water circulation and pumping energy waste.

[0019] 2. This invention sets up a dehumidification reliability model and a position-preserving and anti-shaking mechanism. Within a sliding time window, it compares the theoretical dehumidification flow rate with the measured drainage flow rate and generates dehumidification reliability based on the mass conservation deviation. When the reliability drops to the zero threshold, it issues the highest priority position-preserving command, forcibly shields conflicting valve position signals and locks the current valve position, preventing distortion of underlying data from inducing oscillation and divergence of the regulating valve and collapse of the hydraulic network control.

[0020] 3. This invention sets up a supply and demand two-dimensional mapping model and a chilled water real-time flow optimization model. It decouples the actual external load demand by using the difference between the inlet dew point and the moisture content. It uses the geometric mean of the cold air coupling degree and the latent heat conversion efficiency to characterize the internal operating efficiency. It calculates the scaling factor without self-excitation risk based on the rated flow rate as the open-loop anchor point, thereby achieving a precise match between cooling supply and dehumidification demand and ensuring the system's operational stability under all operating conditions. Attached Figure Description

[0021] The invention will now be further described with reference to the accompanying drawings.

[0022] Figure 1 This is a flowchart of the entire invention;

[0023] Figure 2 This is a flowchart of the cold air coupling and latent heat conversion evaluation process of the present invention;

[0024] Figure 3 This is a flowchart of the supply and demand bidirectional mapping and dehumidification reliability diagnosis of the present invention;

[0025] Figure 4 This is a flowchart of the real-time cold water flow optimization and execution process of the present invention;

[0026] Figure 5 This is a schematic diagram of the operating status of the flow execution mechanism and the hardware anti-shake self-locking monitoring interface in an embodiment of the present invention;

[0027] Figure 6 This is a schematic diagram of the real-time calculation result interface of the multi-dimensional evaluation model of the control module in an embodiment of the present invention;

[0028] Figure 7 This is a schematic diagram of the running trend monitoring curve of the core decoupling parameters in an embodiment of the present invention. Detailed Implementation

[0029] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below in conjunction with specific embodiments.

[0030] like Figures 1 to 4 As shown, the ground source heat pump coupled fresh air dehumidification system of the present invention includes:

[0031] Sensing Module: Used to collect air-side and water-side operating parameters, including an inlet water temperature sensor installed in the chilled water inlet pipe section of the fresh air dehumidifier to obtain the real-time chilled water inlet temperature; a frontal anemometer installed on the windward side of the surface cooler to obtain the real-time frontal wind speed; a condensate flow meter installed in the drain riser of the water tray to obtain the instantaneous drainage flow rate; inlet air temperature, humidity, and dew point sensors installed in the intake section to obtain the inlet dry-bulb temperature, inlet relative humidity, and inlet dew point temperature; outlet air temperature and humidity sensors installed in the supply section to obtain the outlet dry-bulb temperature and outlet relative humidity; a surface temperature sensor installed on the coil surface to obtain the coil surface dry-bulb temperature; and a chilled water flow meter installed in the return water section to obtain the real-time chilled water volumetric flow rate.

[0032] Control module: interconnected with the sensing module via a communication bus, internally encapsulating a cold air coupling model, a latent heat conversion model, a supply-demand two-dimensional mapping model, a dehumidification reliability model, and a chilled water real-time flow optimization model; the control module is configured to generate source-load synergy and dehumidification reliability based on the acquired operating parameters, and output the target chilled water volume flow rate command;

[0033] Flow actuator: includes an electric regulating valve connected in series in the return water section, the pipeline of which is connected to the manifold of the ground source heat pump host to form a cold water circulation loop; the electric regulating valve is configured to receive the target chilled water volume flow command and perform the corresponding valve core displacement action.

[0034] In actual operation, firstly, the sensing module begins to collect all operating parameters. The inlet water temperature sensor acquires the chilled water inlet temperature, the oncoming anemometer measures the oncoming wind speed of fresh air passing through the surface cooler, the condensate flow meter begins to record the instantaneous drainage flow rate, and at the same time, the inlet air temperature, humidity and dew point sensors acquire the inlet air dry bulb temperature, inlet air relative humidity and inlet air dew point temperature entering the system, the outlet air temperature and humidity sensors acquire the processed outlet air dry bulb temperature and outlet air relative humidity, the coil surface temperature sensor monitors the surface temperature of the surface cooler coil, and the chilled water flow meter monitors the chilled water volume flow rate through the surface cooler in real time. These data are transmitted to the control module in real time.

[0035] After receiving these operating parameters, the control module immediately activates its internally encapsulated models for calculation and analysis. The cold air coupling model evaluates the coupling efficiency of the current cold air and dehumidification process based on parameters such as the oncoming wind speed, inlet air temperature, and cold water inlet temperature. The latent heat conversion model calculates the effectiveness of converting cold energy into latent heat for dehumidification based on the temperature and humidity data of the inlet and outlet air and the surface temperature of the coil. The supply and demand two-dimensional mapping model comprehensively evaluates the current external load demand (e.g., calculated based on the difference between the inlet air dew point temperature and the absolute moisture content of the inlet and outlet air) and the internal operating effectiveness of the system (e.g., calculated based on the cold air coupling degree and the latent heat conversion effectiveness). The dehumidification reliability model verifies the physical conservation of the dehumidification process by comparing the theoretical moisture extraction flow rate with the measured drainage flow rate measured by the condensate flow meter, thereby generating dehumidification reliability. For example, if the measured drainage flow rate is much lower than the theoretical moisture extraction flow rate, the dehumidification reliability will decrease, indicating that there may be a sensor malfunction or drainage abnormality.

[0036] Based on these calculations, the control module generates source-load synergy and dehumidification reliability. If the source-load synergy indicates that the current cooling supply and dehumidification load are not well matched, or the dehumidification reliability is low (e.g., due to abnormal condensate flow meter data), the control module will adjust its decision logic. The chilled water real-time flow optimization model comprehensively considers these evaluation indicators and calculates an optimal target chilled water volume flow command. For example, if the dehumidification reliability is normal and the external load demand is high, and the internal operating efficiency is also high, the optimization model may calculate a larger target chilled water volume flow to enhance the dehumidification capacity.

[0037] Finally, the flow actuator receives the target chilled water volume flow command output by the control module. The internal servo motor of the electric regulating valve drives the valve core to make corresponding displacement movements, accurately adjusting the chilled water flow through the surface cooler. If the command requires an increase in flow, the valve core will retract upward, expanding the annular cross-sectional area of ​​the chilled water flow, thereby increasing the actual chilled water flow to meet the dehumidification requirements.

[0038] When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, it extracts fluid and heat exchange conversion parameters. The feature extraction logic is as follows:

[0039] Based on the preset dry air density constant, the effective windward cross-sectional area constant of the surface cooler, and the real-time oncoming wind speed, the dry air mass flow rate is calculated and obtained.

[0040] Based on the inlet dry-bulb temperature and inlet relative humidity, combined with the calculation of water vapor saturation partial pressure and molar mass ratio conversion, the absolute moisture content of the inlet air is calculated and obtained. Based on the outlet dry-bulb temperature and outlet relative humidity, combined with the calculation of water vapor saturation partial pressure and molar mass ratio conversion, the absolute moisture content of the outlet air is calculated and obtained.

[0041] Based on the isobaric specific heat capacity constant of dry air and water vapor and the latent heat of vaporization of water, combined with the dry-bulb temperature and absolute moisture content of the corresponding measuring points, the specific enthalpy of the inlet air and the specific enthalpy of the outlet air are calculated and obtained respectively, and the specific enthalpy of saturated air at the average temperature of the coil surface is calculated based on the dry-bulb temperature of the coil surface.

[0042] The difference between the enthalpy of the incoming air and the enthalpy of the outgoing air is used as the first calculation item. The difference between the enthalpy of the intake air and the enthalpy of the saturated air on the coil surface is used as the second calculation item. The dehumidification contact coefficient is calculated by the proportional relationship between the first calculation item and the second calculation item.

[0043] Using the first calculation term as the numerator and the sensible heat change obtained by multiplying the temperature difference between the inlet and outlet dry bulbs by the constant pressure specific heat capacity constant as the denominator, the moisture extraction coefficient is calculated.

[0044] In the second calculation term of the dehumidification contact coefficient and the denominator of the dehumidification coefficient, a preset minimum bias constant is simultaneously substituted into the summation operation.

[0045] When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, the calculation formula for the internal fluid and heat transfer conversion parameters is as follows:

[0046]

[0047]

[0048]

[0049]

[0050]

[0051]

[0052]

[0053] in, Dry air mass flow rate, unit: ; The preset dry air density constant, in units of: ; Real-time oncoming wind speed, unit: ; This is the preset effective windward cross-sectional area constant of the surface cooler, in units of: ; To obtain the absolute moisture content, the control module substitutes the dry-bulb temperature and relative humidity of the incoming air into the input data. Substitute the outlet dry bulb temperature and outlet relative humidity into the equation to obtain the outlet absolute moisture content. The unit is: ; The ratio of the molar mass of water vapor to that of dry air is a dimensionless constant. Relative humidity, dimensionless; For temperature The partial pressure of saturated water vapor at the specified value is expressed in units of: ; Dry bulb temperature, in units of: ; The preset local atmospheric pressure constant, in units of: ; , , The constants for fitting the pre-defined Antoine equation are dimensionless. and These are the specific enthalpy of the inlet and outlet air, respectively, in units of: ; The enthalpy of saturated air at the average temperature of the coil surface is expressed in units of: ; , These are the inlet dry bulb temperature and the outlet dry bulb temperature, respectively, in units of: ; The dry-bulb temperature of the coil surface, in units of: ; This represents the saturated absolute moisture content corresponding to the surface temperature of the coil, in units of: ; The dehumidification contact coefficient is dimensionless. The moisture extraction coefficient is dimensionless. , These are the preset isobaric specific heat capacity constants for dry air and water vapor, respectively, in units of: ; The preset latent heat of vaporization of water is expressed in units of: ; The preset bias constant, in units of: .

[0054] This judgment condition is a prerequisite for activating subsequent calculations of fluid and heat exchange conversion parameters. It ensures that detailed heat and moisture exchange analysis is only performed when the surface cooler actually cools and dehumidifies, avoiding unnecessary complex calculations under non-dehumidification conditions. This improves the system's computational efficiency and response speed. This judgment can be implemented through the logic unit inside the control module, such as through comparator circuits or conditional statements in software to monitor and evaluate inlet and outlet air parameters in real time. These calculation formulas are the core of the control module's quantitative analysis of the heat and moisture exchange process. Based on thermodynamics and heat and mass transfer principles, they transform the raw operating parameters collected by the sensing module into physically meaningful intermediate variables and key performance indicators. These formulas can be pre-programmed in the control module's firmware or executed by software algorithm modules on hardware platforms such as programmable logic controllers (PLCs) or industrial computers (IPCs).

[0055] Dry air mass flow rate The calculation formula is used to calculate the dry air mass flow rate through the surface cooler. The dry air mass flow rate is a fundamental parameter characterizing air handling capacity and is crucial for subsequent heat and humidity load calculations.

[0056] in, The preset dry air density constant can be set by looking up a table or by using empirical values. Real-time oncoming wind speed is obtained in real time by the oncoming anemometer in the sensing module. The preset effective windward cross-sectional area constant of the surface cooler is an inherent geometric parameter of the surface cooler. This calculation can be efficiently completed by the floating-point unit or dedicated digital signal processor (DSP) in the control module.

[0057] Absolute moisture content The calculation formula is used to calculate the absolute moisture content of air, which is the mass of water vapor in a unit mass of dry air. Absolute moisture content is an indicator of air humidity and directly reflects the air's ability to hold water. The control module adjusts the inlet dry bulb temperature... relative humidity of incoming air Substitute to obtain the absolute moisture content of the incoming air The temperature of the dry bulb will be determined. relative humidity of the air outlet Substitute the values ​​to obtain the absolute moisture content of the outlet air. .

[0058] in, The ratio of the molar mass of water vapor to that of dry air is a constant. Relative humidity is obtained from either an inlet air temperature and humidity sensor and a dew point sensor, or an outlet air temperature and humidity sensor. For temperature The saturated water vapor partial pressure at a given temperature can be calculated using the Antoine equation or other fitting formulas. This is the preset local atmospheric pressure constant.

[0059] Enthalpy of intake air The formula is used to calculate the specific enthalpy of incoming air. Specific enthalpy is the total energy contained per unit mass of air, including sensible heat and latent heat. It is an important parameter for assessing the thermal and humid state of air. The preset specific heat capacity constant of dry air at constant pressure. The inlet dry bulb temperature is obtained from inlet air temperature, humidity, and dew point sensors. The absolute moisture content of the intake air is calculated using the above formula. The preset latent heat of water vaporization constant, This is the preset isobaric specific heat capacity constant of water vapor.

[0060] Specific enthalpy of saturated air at the average temperature of the coil surface The calculation formula is used to calculate the saturated air specific enthalpy at the average temperature of the coil surface. This parameter represents the energy level of air when it comes into contact with the coil surface and reaches saturation. It is the theoretical limiting state of the heat and moisture exchange process.

[0061] in, The dry-bulb temperature of the coil surface is obtained from the coil surface temperature sensor. Coil surface temperature The corresponding saturated absolute moisture content can be calculated under saturated conditions using the above absolute moisture content formula.

[0062] Dehumidification contact coefficient The calculation formula is used to calculate the dehumidification contact coefficient, which is a dimensionless parameter used to quantify the efficiency of heat and moisture exchange between air and the surface of the cooler. It reflects the degree to which the state point of the air moves toward the saturation line when it passes through the cooler.

[0063] in, The specific enthalpy of the outlet air is calculated using the same method as... Similarly, using and ; This is a preset bias constant used to avoid a denominator of zero or to handle extreme cases; the moisture extraction coefficient. The calculation formula is used to calculate the moisture extraction coefficient, a dimensionless parameter that characterizes the relative proportion of latent heat exchange to sensible heat exchange during the dehumidification process of the surface cooler. It is a key indicator for evaluating dehumidification performance. The outlet dry bulb temperature is obtained from the outlet air temperature and humidity sensor. This is a preset bias constant.

[0064] When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, i.e., when the system is in cooling and dehumidification mode, it will activate these calculations. First, it will use the real-time oncoming wind speed obtained by the sensor module. and the preset dry air density constant and the effective windward cross-sectional area constant of the surface cooler Calculate the dry air mass flow rate This provides an accurate airflow reference for subsequent heat and humidity load calculations.

[0065] Next, the dry bulb temperatures of the inlet and outlet air are obtained through inlet air temperature and humidity sensors and dew point sensors, and outlet air temperature and humidity sensors. , and relative humidity , The ratio of the molar mass of water vapor to that of dry air is constant. ,temperature The saturated water vapor partial pressure below and the preset local atmospheric pressure constant Accurately calculate the absolute moisture content of the incoming air. Absolute moisture content of the exhaust air These absolute moisture contents are the core indicators for quantifying the water vapor content in the air, and directly reflect the dehumidification capacity.

[0066] Based on this, the control module further calculates the specific enthalpy of the intake air. Enthalpy of exhaust air and the enthalpy of saturated air at the average temperature of the coil surface These specific enthalpy values ​​combine the sensible and latent heat of air, and can comprehensively describe the energy state of air as it enters, leaves the surface cooler, and comes into contact with the coil surface.

[0067] Among them, the dry bulb temperature of the coil surface Provided by the coil surface temperature sensor, the control module can further calculate the dehumidification contact coefficient using these specific enthalpy values. and dehumidification coefficient Dehumidification contact coefficient The efficiency of heat and moisture exchange between air and the surface of the cooler was quantified, while the moisture extraction coefficient... This characterizes the relative proportion of latent heat exchange and sensible heat exchange during the dehumidification process. Through the above series of calculations, the control module can transform the raw operating parameters collected by the sensing module into intermediate variables and key performance indicators with clear physical meaning, thereby getting rid of the limitations of traditional control methods that rely solely on simple feedback of indoor return air temperature and humidity.

[0068] The data processing logic for the cold air coupling model and the latent heat conversion model is as follows:

[0069] The cold air coupling model uses the ratio between the real-time oncoming wind speed and the preset rated oncoming wind speed as the first input item. The ratio of the temperature difference between the inlet dry bulb temperature and the real-time chilled water inlet temperature to the preset rated heat transfer temperature difference is used as the second input item. ), calculate the deviation of the ratio of the first input item to the second input item relative to the preset ratio constant, and calculate the output cold air coupling degree based on the deviation through a nonlinear attenuation function;

[0070] The latent heat conversion model performs algebraic constraint mapping calculation on the dehumidification coefficient to extract the latent heat share weight; the latent heat share weight is multiplied and weighted with the dehumidification contact coefficient to calculate and output the latent heat conversion effectiveness.

[0071] The calculation formulas for the cold air coupling model and the latent heat conversion model are as follows:

[0072]

[0073]

[0074] in, The coupling degree of cold air is dimensionless. This refers to the real-time chilled water inlet temperature, expressed in units of: ; The preset rated oncoming wind speed, in units of: ; The preset difference between the rated intake air temperature and the water temperature, in units of: ; The preset attenuation coefficient is dimensionless. The preset optimal cold air ratio constant is dimensionless. The latent heat conversion validity is dimensionless.

[0075] The cold-air coupling model is used to quantify the matching degree between the air and water sides in the heat exchange process of the surface cooler. This model can be constructed based on pre-established empirical formulas, simplified models based on physical mechanisms, or functional relationships obtained by fitting a large amount of experimental data. The latent heat conversion model is also a mathematical model, which is used to evaluate the efficiency of the system in converting cold energy into latent heat during the dehumidification process. This model can be constructed based on theoretical formulas from enthalpy-humidity diagram analysis, modified models combined with actual operating data, or conversion laws obtained through computational fluid dynamics (CFD) simulations.

[0076] Cold air coupling The model is built based on the efficiency-to-number of heat transfer units ( The theory, in which the dimensionless wind speed term in the formula ( Positively correlated with the convective heat transfer coefficient of the air-side surface, representing the heat transfer motive force, dimensionless temperature difference term ( The ratio represents the heat transfer driving potential between the hot and cold fluids. The physical equivalent of their ratio is the heat capacity ratio in the heat transfer process of the surface cooler. This ratio is then compared with the optimal cold air ratio constant. By performing deviation calculations, we can objectively assess whether the current operating conditions have deviated from the optimal heat transfer impedance matching point of the surface cooler, thus providing an aerodynamic and thermodynamic basis for the subsequent calculation of latent heat conversion efficiency.

[0077] Cold air coupling It is a dimensionless index that represents the degree of matching between cold air and cold water in the heat exchange process. It can reflect the coordination between the current air volume and cooling capacity configuration. This index can be calculated in real time by the calculation module inside the control module, or obtained by looking up the table based on the input parameters.

[0078] Latent heat conversion validity It is a dimensionless index that represents the efficiency of the system in converting cold energy into latent heat during the dehumidification process. It can reflect the effectiveness of the system in handling wet loads. This index can be calculated in real time by the calculation module inside the control module.

[0079] Real-time chilled water inlet temperature This refers to the actual temperature of the chilled water entering the surface cooler. Its function is to serve as a key input parameter in the cold air coupling model, reflecting the energy supply status on the cold source side. This temperature can be obtained in real time through an inlet water temperature sensor installed in the chilled water inlet pipe section.

[0080] Preset rated oncoming wind speed This refers to the reference value of the airflow velocity on the windward side of the surface cooler under the system's design or optimal operating conditions. Its function is to serve as a benchmark parameter in the cold air coupling model for comparison with the real-time wind speed. This parameter can be set during the system commissioning phase according to design requirements or experimental data and stored in the non-volatile memory of the control module.

[0081] Preset rated air intake temperature difference This refers to the reference temperature difference between the inlet dry bulb temperature and the chilled water inlet temperature under the system's design or optimal operating conditions. Its function is to serve as a benchmark parameter in the cold air coupling model for comparison with the real-time temperature difference. This parameter can be set during the system commissioning phase according to design requirements or experimental data and stored in the non-volatile memory of the control module.

[0082] Preset attenuation coefficient It is a dimensionless constant used to adjust the penalty degree when the cold air coupling degree deviates from the optimal ratio in the cold air coupling degree model. Its function is to control the sensitivity of the cold air coupling degree to parameter deviation. This coefficient can be set through system simulation, experimental optimization or expert experience. Its value range is set from 0.5 to 1.5. The specific value is experimentally calibrated according to the geometric characteristics of the surface cooler fin spacing and stored in the control module.

[0083] Preset optimal cooling air ratio constant It is a dimensionless constant that represents the ideal proportional relationship between the wind speed ratio and the temperature difference ratio under optimal operating conditions. Its function is to serve as a reference point in the cold air coupling model, guiding the system to operate under optimal conditions. This constant can be determined through system design theory calculations, experimental data analysis, or CFD simulations. Its typical value range is 0.85 to 1.15. It characterizes the optimal matching ratio between the air-side convective heat transfer intensity and the water-side cooling supply intensity and is stored in the control module.

[0084] Dehumidification contact coefficient It is a dimensionless coefficient that represents the effectiveness of heat and mass transfer between air and a wet surface. Its function is to reflect the efficiency of heat exchange on the air side. This coefficient can be calculated by the ratio of the change in enthalpy on the air side to the enthalpy difference.

[0085] Moisture extraction coefficient It is a dimensionless coefficient that represents the relative proportion of sensible heat and latent heat exchange during the dehumidification process of air. Its function is to reflect the effectiveness of the dehumidification process. This coefficient can be calculated by the ratio of the change in enthalpy to the change in sensible heat on the air side.

[0086] This solution, through the cold air coupling model and latent heat conversion model encapsulated within the control module, can utilize real-time operating parameters collected by the sensing module, such as the real-time chilled water inlet temperature. Real-time oncoming wind speed Inlet dry bulb temperature And so on, as well as the dehumidification contact coefficient obtained through calculation. and dehumidification coefficient Accurately calculate the cold air coupling degree and latent heat conversion validity .

[0087] Cold air coupling By comparing the ratios of real-time wind speed to rated wind speed and real-time temperature difference to rated temperature difference, and combining this with the optimal cooling air ratio constant... and attenuation coefficient This quantifies the degree of matching between the current airflow and water flow in the heat exchange boundary layer.

[0088] Latent heat conversion validity Then utilize the dehumidification contact coefficient and dehumidification coefficient The nonlinear function relationship was used to evaluate the true proportion of cooling capacity converted into latent heat of pure dehumidification. By introducing these two indicators, the control module no longer relies solely on simple temperature and humidity feedback, but can deeply analyze the energy coupling and conversion efficiency within the system. This allows for a more refined and comprehensive evaluation of the operating status of the ground source heat pump coupled fresh air dehumidification system. This quantitative evaluation capability enables the system to accurately determine whether the current cooling capacity distribution is in an optimal state from the perspective of energy utilization, providing a scientific basis for subsequent flow regulation and effectively solving the problem of insufficient perception of the heat exchange process in traditional control.

[0089] The control module is configured based on the cold air coupling degree. With latent heat conversion validity The control module is configured based on the cold air coupling degree. With latent heat conversion validity Executing adjustment steps means having the ability to adaptively control based on system performance indicators, rather than simply using a preset program. (Cooling coupling degree) This reflects the efficiency of the surface cooler in sensible heat transfer, while the latent heat conversion efficiency... This measures the system's ability to effectively convert cooling capacity into latent heat for dehumidification. These two indicators comprehensively evaluate the system's operating status and efficiency. The following adjustment steps should be performed:

[0090] S11: Control module reads cold air coupling degree With latent heat conversion validity The value;

[0091] Read operations can be implemented via internal bus or memory access to ensure that the latest calculation results are obtained. For example, the control module can periodically retrieve these values ​​from its internal memory, or update and read them immediately after each calculation is completed.

[0092] S12: When a determination is made or When the temperature drops to the preset lower control threshold, the control module sends an opening limit command to the electric regulating valve.

[0093] The "preset control lower limit threshold" here is a critical value determined during system design based on experience, experiments, or simulations. It indicates that intervention is needed when the system's operating performance falls below this value. For example, this threshold could be a percentage value, such as when... or When the opening is below 70% of its rated value, the control module issues an opening limit command, which means that it generates a specific digital or analog signal and sends it to the electric regulating valve through the communication bus, instructing it to limit the opening of the valve core.

[0094] S13: After receiving the opening limit command, the internal servo motor of the electric regulating valve drives the valve core to move downward and enter the valve position limit state, reducing the internal cold water flow area.

[0095] Electric control valves typically include a servo motor or stepper motor for precise control of the valve spool position. Upon receiving a command, the servo motor drives the valve spool to move in the closing direction until a preset limit position is reached. This limit can be a physical limit or a maximum closing degree set by software, designed to reduce the flow of chilled water through the surface cooler, thereby reducing cooling output.

[0096] By introducing cold air coupling With latent heat conversion validity As an evaluation indicator of system operation status, it realizes real-time monitoring of the operating efficiency of the ground source heat pump coupled fresh air dehumidification system. Based on the air-side and water-side operating parameters collected by the sensor module, the control module can use the cold air coupling model and the latent heat conversion model to calculate these two key indicators in real time. When any of these indicators falls to the preset control lower limit threshold, it indicates that the current heat exchange efficiency or dehumidification capacity of the system can no longer meet the requirements of high-efficiency operation, and there may be a mismatch between the cooling output and the actual demand.

[0097] At this point, the control module no longer relies solely on temperature and humidity deviations for adjustment. Instead, it actively sends an opening limit command to the electric regulating valve in the flow actuator. Upon receiving this command, the internal servo motor of the electric regulating valve drives the valve core downward, entering the valve position limit state. This forcibly reduces the flow area of ​​the cold water passing through the surface cooler. This feedback regulation mechanism based on performance indicators effectively prevents the system from blindly operating under inefficient conditions. By limiting the valve opening, it suppresses the output of ineffective cooling capacity and prevents energy waste caused by over-regulation. This solution, combined with the basic sensing module, control module, and flow actuator, forms a closed-loop intelligent control system. This allows the system to more accurately assess its own performance and take timely intervention measures when facing complex and variable fresh air loads, thereby improving the system's operational stability and energy utilization efficiency under complex conditions.

[0098] The feature extraction logic of the supply-demand two-dimensional mapping model and the dehumidification reliability model is as follows:

[0099] The supply and demand two-dimensional mapping model converts the inlet air dew point temperature and the reference inlet air dew point temperature into absolute temperatures, calculates the ratio of the converted inlet air dew point temperature to the reference inlet air dew point temperature, multiplies the ratio by the ratio of the difference between the absolute moisture content of the inlet air and the target absolute moisture content to the difference between the rated moisture content, extracts the load bias factor, performs a bounded mapping operation on the load bias factor through an algebraic smoothing activation function, outputs the external load demand degree, and calculates the square root of the product of the cold air coupling degree and the latent heat conversion effectiveness to output the internal operating effectiveness.

[0100] The dehumidification reliability model calculates the theoretical average moisture extraction flow rate, determined by the difference between the dry air mass flow rate and the absolute moisture content of the inlet and outlet air, within a preset discrete sliding time window. It also calculates the measured average drainage flow rate collected by the condensate flow meter. The deviation between the theoretical average moisture extraction flow rate and the measured average drainage flow rate is reciprocally decayed using a fractional calculation logic with bidirectional symmetry to output the dehumidification reliability.

[0101] The calculation formulas for the supply-demand two-dimensional mapping model and the dehumidification reliability model are as follows:

[0102]

[0103]

[0104]

[0105]

[0106]

[0107]

[0108] in, The load bias factor is dimensionless. This refers to the inlet dew point temperature, in units of: ; The preset reference inlet dew point temperature, in units of: ; The dehumidification requirement has a different moisture content, and The unit is: ;in The preset target absolute humidity content of the supply air represents the set humidity benchmark required by the environment. The preset absolute moisture content difference between the inlet and outlet air is expressed in units of: ; The preset response steepness coefficient is dimensionless. The preset load activation threshold is dimensionless. External load demand is dimensionless. For internal operating validity, dimensionless; For dehumidification reliability, dimensionless; This represents the total number of samples taken within the preset sliding window, and is dimensionless. This is the sampling sequence number, which is dimensionless. The theoretical average wettability within the sliding time window, in units of: ; For the condensate flow meter at the first The instantaneous drainage flow rate obtained in this sampling, in units of: ; The measured average drainage flow rate within the sliding time window, in units of: ; The preset mass bias constant, in units of: ; The preset deviation penalty index is dimensionless.

[0109] The supply-demand two-dimensional mapping model is a mathematical model used to quantify external dehumidification demand and internal operating efficiency. It can be encapsulated in the software algorithm of the control module and implemented through programming. The dehumidification reliability model is a model used to evaluate the reliability of the dehumidification process. It can also be implemented as a software module or hardware acceleration unit inside the control module. The authenticity of the system operation is judged by real-time monitoring and comparison of data.

[0110] Load bias factor It is a dimensionless parameter used to characterize the degree of deviation of the current environment from the dehumidification load, and its calculation depends on the inlet dew point temperature. Reference intake dew point temperature The difference in absolute moisture content between the inlet and outlet air The difference in absolute moisture content between the rated inlet and outlet air Response steepness coefficient and load activation threshold .

[0111] Inlet dew point temperature It is an important indicator for measuring the water vapor content in the air, which can be obtained in real time by the intake air temperature, humidity and dew point sensors installed in the direct section of the air intake, with reference to the intake air dew point temperature. The difference between the absolute moisture content of the inlet and outlet air and the rated moisture content These are the baseline parameters preset during system design, and are usually stored in the non-volatile memory of the control module.

[0112] Response steepness coefficient and load activation threshold These are configurable parameters used to adjust the model's sensitivity to load changes and activation conditions, including the response steepness coefficient. The value ranges from 1.0 to 3.0, and is used to amplify load sensitivity under high humidity conditions; load activation threshold. The value is set to a range of 0.05 to 0.15 as a dead zone buffer to prevent frequent start-ups and shutdowns of the system under slight load fluctuations, based on the external load demand. It is the load bias factor The normalized result is usually expressed as a value between 0 and 1, reflecting the actual intensity of the current environmental demand for dehumidification.

[0113] Internal operating validity It is a comprehensive indicator used to evaluate the efficiency of heat exchange and dehumidification within the system, measured by the cold air coupling degree. and latent heat conversion validity The geometric mean was calculated.

[0114] Dehumidification reliability It is a key self-diagnostic parameter used to determine the reliability of the system's dehumidification process. It is determined by comparing the theoretical average dehumidification flow rate. and measured average drainage flow rate To calculate.

[0115] Total number of sliding window samples The number of data points used to calculate the average flow rate is defined and can be configured according to system response speed and data smoothing requirements. The sampling sequence number is also specified. It is the index of the data points within the sliding window.

[0116] Theoretical average wet flow rate The theoretical dehumidification capacity is calculated based on the airflow rate and the difference in absolute moisture content between the inlet and outlet air, while the actual measured average drainage flow rate is... This is the instantaneous drainage flow rate obtained from the condensate flow meter. It is obtained by performing a moving average.

[0117] mass bias constant It is a small positive value used to avoid the denominator being zero in the calculation formula when the flow rate is close to zero, thus improving the numerical stability of the model. (Bias penalty index) It is an adjustable parameter used to control the dehumidification reliability when the theoretical value differs from the measured value. The degree of sensitivity to decline.

[0118] Specifically, the control module first uses the intake dew point temperature obtained by the sensor module. Inlet dry bulb temperature Relative humidity of incoming air Outlet dry bulb temperature Relative humidity of the air outlet Calculate the absolute moisture content difference between the inlet and outlet air using parameters such as these. .

[0119] Subsequently, these parameters are substituted into the supply and demand two-dimensional mapping model to generate the load bias factor. And further mapped to external load demand. This process can accurately quantify the actual dehumidification needs of the current environment, avoiding the deviation caused by relying solely on a single temperature and humidity parameter.

[0120] Meanwhile, the control module calculates the cold air coupling degree by combining the cold air coupling model and the latent heat conversion model. With latent heat conversion validity Internal operational validity was obtained by calculating the geometric mean. This internal operational validity comprehensively reflects the current heat exchange and dehumidification potential of the system, providing an internal benchmark for subsequent supply and demand matching.

[0121] Based on this, the control module obtains the instantaneous drainage flow rate through the condensate flow meter. The measured average drainage flow rate within the sliding time window was calculated. Meanwhile, based on the real-time oncoming wind speed Inlet dry bulb temperature Relative humidity of incoming air Outlet dry bulb temperature Relative humidity of the air outlet Using parameters such as these, the theoretical average wettability within the sliding time window was calculated. .

[0122] Finally, and Substitute the values ​​into the dehumidification reliability model to calculate the dehumidification reliability. This dehumidification reliability incorporates a physical process conservation check, utilizing a bias penalty index. By handling the inconsistency between measured and theoretical data with sensitivity processing, the system can effectively identify abnormal operating conditions such as sensor drift, pipeline blockage, or condensate splashing. This approach, which compares external requirements with actual internal operational validity and uses dehumidification confidence as a confidence index, enables the system to have self-diagnostic capabilities. It ensures that control commands are generated based on real and effective physical states, significantly improving the system's operational reliability and adjustment accuracy under complex operating conditions.

[0123] The control module is configured to operate based on dehumidification reliability. Perform the following adjustment steps:

[0124] Step S21: The control module reads the calculated dehumidification reliability. ;

[0125] The control module uses its internal dehumidification reliability model, combined with operating parameters collected by the sensor module (such as the instantaneous drainage flow rate obtained from the condensate flow meter), to... Dry air mass flow rate The difference in absolute moisture content between the inlet and outlet air (etc.), to calculate the dehumidification reliability. Reading this confidence value is the basis for subsequent judgment of the system's operating status and the implementation of corresponding control strategies. This reading process can be completed through internal register access, memory address reading, or through specific function calls.

[0126] Step S22: When determining the dehumidification reliability When the value drops to the preset zero threshold range, the control module sends a position-holding and anti-shake command to the electric regulating valve. The position-holding and anti-shake command has the highest control priority and forcibly blocks and overrides the valve core displacement command generated by the system based on other validity indicators.

[0127] When determining the reliability of dehumidification When the system dehumidification reliability drops to a preset zero-point threshold range, the zero-point threshold range refers to a pre-defined numerical range that represents an extremely low or unreliable level of system dehumidification reliability. Entering this threshold range indicates potential issues such as severe sensor data distortion, physical process abnormalities (e.g., clogged drain pipes, severe condensate runoff), or control logic deviations. Continuing with routine dynamic adjustments at this point could lead to negative consequences. To prevent underlying data distortion from causing other calculated indicators, such as cold air coupling, to malfunction simultaneously, the position-maintaining and anti-shake command is given the highest priority within the control module. Once triggered, it will forcibly block and override limit or flow-expanding commands based on other internal validity indicators, preventing the actuator from receiving conflict signals. This zero-point threshold range can be a fixed numerical interval, for example... ,in It can be a very small positive number, or the threshold range can be dynamically adjusted, for example, adaptively determined based on historical operating data or system load.

[0128] Step S23: After receiving the position-holding and anti-shake command, the actuator of the electric regulating valve cuts off the response to the dynamic regulation electrical signal and performs the position-holding action, fixing the valve core displacement at the current moment with the internal self-locking mechanism.

[0129] The control module sends a position-holding and anti-shake command to the electric regulating valve. The purpose of this command is to instruct the electric regulating valve to stop its current dynamic regulating behavior and keep its valve core in its current position to prevent frequent actions or oscillations caused by erroneous or unstable control signals. This command can be a specific digital signal code, such as a high-level signal or a specific data packet.

[0130] After receiving a position-holding and anti-jitter command, the actuator motor of the electric control valve, which is the core component driving the valve core displacement, typically a stepper motor, DC motor, or servo motor, converts electrical signals into mechanical motion, thereby changing the valve core position. Upon receiving the position-holding and anti-jitter command, the actuator motor will change its operating state according to the command content and will no longer respond to regular flow regulation signals.

[0131] Cut off the response to the dynamic adjustment electrical signal, which refers to the control module responding to system operating parameters (such as the target chilled water volume flow rate command). The electrical signals are calculated in real time and sent to the electric regulating valve to adjust the valve core position to change the chilled water flow. Cutting off the response to these signals means that the control circuit or actuator of the electric regulating valve no longer processes these regular regulating signals, thereby preventing the valve core from moving according to these signals. This can be achieved by physically disconnecting the signal path by setting an electronic switch or relay inside the electric regulating valve.

[0132] The position holding action refers to the electric regulating valve maintaining its valve core in the current position after receiving the position holding and anti-shake command, without making any active displacement adjustment. This can be achieved by maintaining the excitation state of the actuator motor (for stepper motors or servo motors) to generate holding torque.

[0133] The valve core displacement is fixed by an internal self-locking mechanism. The internal self-locking mechanism is a mechanical structure inside the electric regulating valve. It can automatically lock the valve core in the current position after the actuator stops driving or the power is cut off, preventing the valve core from being displaced due to fluid pressure, vibration or other external forces. Common internal self-locking mechanisms include worm gear transmission mechanisms, which are irreversible, or ratchet and pawl mechanisms, electromagnetic brakes or friction brakes. These mechanisms can provide sufficient locking force in the non-driving state.

[0134] The data processing logic of the real-time cold water flow optimization model is as follows:

[0135] The real-time chilled water flow optimization model uses the preset rated chilled water volumetric flow rate as the benchmark value to extract the external load demand, internal operating efficiency, and dehumidification reliability.

[0136] The product of the dehumidification confidence level and the external load demand level is calculated as the first adjustment weight. The product of the dehumidification reliability and the internal operational validity is calculated as the second moderating weight. Based on the numerator containing the first adjustment weight and the denominator containing the second adjustment weight, the flow scaling factor is calculated and obtained;

[0137] The preset rated chilled water volumetric flow rate is multiplied by the flow rate scaling factor to output the target chilled water volumetric flow rate command normally. When the dehumidification confidence approaches the preset zero-point threshold, the flow rate scaling factor approaches one, so that the value of the generated target chilled water volumetric flow rate command is equal to the preset rated chilled water volumetric flow rate.

[0138] The calculation formula for the real-time flow optimization model of cold water is as follows:

[0139]

[0140] in, The value of the target chilled water volumetric flow rate command generated by the control module is in units of: ; The preset rated chilled water volumetric flow rate, in units of: This represents the standard chilled water requirement of the system under design conditions, expressed in units of: ; This is a preset proportional gain coefficient, which is dimensionless.

[0141] This real-time chilled water flow optimization model is a computer mechanism for dynamically adjusting the chilled water flow in a ground source heat pump coupled fresh air dehumidification system. Its core lies in integrating multi-dimensional operating parameters to make real-time corrections to the current chilled water flow, so as to generate target flow instructions that adapt to the current operating status of the system and external load requirements. This model can be encapsulated and executed within the control module based on a preset mathematical algorithm.

[0142] Target chilled water volume flow rate command It is the final result calculated by the real-time chilled water flow optimization model, representing the ideal chilled water flow rate that the system should supply to the surface cooler under the current operating conditions. This instruction, as a control signal issued by the control module to the flow actuator, directly determines the opening degree of the electric regulating valve, thereby precisely controlling the chilled water flow rate through the surface cooler. This instruction can be a continuously changing analog signal or a quantized digital signal to adapt to the control interface of different types of electric regulating valves.

[0143] Preset rated chilled water volume flow rate This refers to the standard chilled water demand of the system under design conditions. This parameter serves as one of the inputs to the real-time chilled water flow optimization model and is the benchmark for dynamic correction of the model.

[0144] Proportional adjustment gain coefficient It is a preset dimensionless constant used to adjust the cold water real-time flow optimization model to the external load demand. Internal operational validity and dehumidification reliability The response strength of the correction factor, the setting of which directly affects the system's sensitivity to changes in operating conditions and the aggressiveness of the adjustment; for example, a larger correction factor... A higher value will make the system respond more quickly to load changes, but may increase the risk of overshoot; a lower value... A certain value makes the system adjustment smoother, but the response may be slower. This coefficient can be optimized through system debugging, analysis of historical operating data, or based on expert experience.

[0145] Dehumidification reliability It is a dimensionless parameter used to quantify the reliability and effectiveness of the current dehumidification process of the system. The calculation of this parameter takes into account the degree of matching between the theoretical dehumidification flow rate and the measured drainage flow rate, and can reflect whether there are problems such as condensate splashing, drainage pipe blockage or sensor data distortion in the system.

[0146] Dehumidification reliability The higher the value, the more reliable the system's dehumidification performance and the more credible the data; conversely, it indicates that there may be an abnormality in the dehumidification process. This parameter provides a basis for the real-time cold water flow optimization model to self-diagnose the system's dehumidification capacity, avoiding blind adjustments when the data is unreliable.

[0147] External load demand This is a dimensionless parameter used to characterize the actual demand intensity of the system's dehumidification capacity in the current environment. The calculation of this parameter integrates environmental factors such as the inlet dew point temperature and the difference in absolute moisture content between the inlet and outlet air, reflecting the magnitude of the external air's moisture load and the degree of external load demand. The higher the value, the more urgent the environmental demand for dehumidification. This parameter provides a quantitative basis for changes in the external environment for the real-time chilled water flow optimization model, enabling the system to actively respond to changes in external moisture load.

[0148] Internal operating validity It is a dimensionless parameter used to evaluate the overall efficiency of cold air coupling and latent heat conversion within the system. The calculation of this parameter incorporates the degree of cold air coupling. and latent heat conversion validity This reflects the extent to which the surface cooler effectively converts sensible heat into latent heat dehumidification capacity under current operating conditions.

[0149] Internal operating validity The higher the value, the higher the dehumidification efficiency of the system. This parameter provides an evaluation basis for the system's own performance in the real-time cold water flow optimization model, enabling the system to make reasonable adjustments according to its own capabilities.

[0150] After the control module receives real-time operating parameters from the sensing module, it first calculates the current dehumidification reliability based on the preset cold air coupling model, latent heat conversion model, supply and demand two-dimensional mapping model, and dehumidification reliability model. External load demand and internal operational validity .

[0151] Subsequently, these parameters were substituted into the calculation formula of the real-time chilled water flow optimization model. The core of this formula lies in comparing the external load demand. With internal operational validity The relative size, and using dehumidification confidence As a weight for adjustment, the preset rated chilled water volumetric flow rate is... Perform dynamic corrections.

[0152] When external load demand Higher than internal operating validity When the external moisture load is high and the system's internal dehumidification capacity is relatively insufficient, the model will calculate a chilled water volumetric flow rate that is higher than the preset rated flow rate. The target chilled water volumetric flow rate command is used to increase the cooling capacity supply and meet dehumidification requirements; conversely, when the external load demand is low... Lower than internal operating validity If this occurs, it indicates that the system's dehumidification capacity may be excessive. In this case, the model will calculate a value lower than the preset rated chilled water volumetric flow rate. The target chilled water volume flow rate instruction is used to reduce the supply of cooling capacity and avoid waste of cooling capacity.

[0153] If dehumidification reliability A lower reading indicates a possible anomaly in the dehumidification process (such as condensate splatter, drain blockage, or sensor distortion), in which case the model will reduce its sensitivity to certain parameters. and The response weights are adjusted to avoid over- or erroneous adjustments based on unreliable data, thereby enhancing the robustness of the system. In this way, the real-time chilled water flow optimization model achieves closed-loop dynamic correction of the target chilled water volume flow rate, so that the output of chilled water flow rate can accurately respond to changes in the external environment's wet load, while also fully taking into account the heat exchange efficiency and the reliability of the dehumidification process within the system.

[0154] The control module is configured to perform the following adjustment steps based on the target chilled water volume flow rate command:

[0155] S31: The control module reads the value of the target chilled water volume flow rate command. ;

[0156] S32: When determining the external load demand Greater than internal operating validity At that time, the control module outputs a positive current amplification signal to the electric regulating valve;

[0157] S33: After receiving a positive flow amplification signal, the internal transmission component of the electric regulating valve drives the valve stem to perform an upward retraction action;

[0158] S34: The valve stem's retraction displacement increases the annular cross-sectional area for cold water flow, adjusting the actual chilled water flow rate through the surface cooler. The corresponding opening degree.

[0159] The control module executes adjustment steps based on the target chilled water volumetric flow rate command. This means that after receiving the optimal chilled water flow rate command calculated by the real-time chilled water flow rate optimization model, the module will initiate a series of preset action procedures to achieve control. The value of the target chilled water volumetric flow rate command... The ideal chilled water flow rate is calculated by the system based on the current operating parameters and optimization model. This serves as the benchmark for flow regulation. The control module reads this value, either by obtaining it from the computing unit via the internal bus or by retrieving it from memory.

[0160] During the adjustment process, the control module will make a crucial determination: the degree of external load demand. Is it greater than internal operating validity? External load demand This reflects the current dehumidification load intensity faced by the system, and its internal operational effectiveness. This characterizes the system's internal efficiency in converting cooling capacity into effective dehumidification latent heat, when the external load demand... Greater than internal operating validity When the system's current cooling capacity or dehumidification capacity is insufficient to meet the needs of the external environment, it is necessary to increase the chilled water flow rate to improve dehumidification performance. At this time, the control module will output a positive flow amplification signal to the electric regulating valve. This signal can be an analog signal, such as a 4-20mA current signal or a 0-10V voltage signal, or a digital pulse signal, to instruct the electric regulating valve to increase the chilled water flow rate.

[0161] After receiving a positive flow-expanding signal, the electric regulating valve's internal transmission component responds to the signal and drives the valve stem to retract upwards. This transmission component may include a servo motor, a reduction gear set, and a lead screw mechanism. By precisely controlling the motor's rotation, linear displacement of the valve stem is achieved. The upward retraction of the valve stem directly increases the annular cross-sectional area of ​​the chilled water flow. This increase in cross-sectional area increases the actual chilled water flow rate through the surface cooler, thereby adjusting the actual flow rate to gradually approach or reach the target chilled water volume flow rate command. The corresponding opening degree.

[0162] Specifically, the control module can employ a high-performance industrial-grade microcontroller, such as an embedded system based on an ARM Cortex-M series processor. This microcontroller integrates a floating-point unit, enabling it to efficiently execute complex calculations such as real-time chilled water flow optimization models, supply-demand two-dimensional mapping models, and dehumidification confidence models, and generate target chilled water volumetric flow rate commands in real time. The microcontroller reads the calculated values ​​from its internal memory or registers. Numerical value, when performing external load demand. With internal operational validity When making comparisons, the microcontroller executes the corresponding logical judgment instructions.

[0163] If the judgment result is The microcontroller outputs an analog voltage signal as a positive current amplification signal through its digital-to-analog converter (DAC) module. For example, it sends a 0-10V voltage signal to an electric regulating valve, which can be an electric ball valve or an electric shut-off valve with an integrated actuator containing a stepper motor or DC servo motor as a transmission component. Upon receiving the analog voltage signal, the motor precisely controls the upward retraction of the valve stem through its internal drive circuit and reduction mechanism. The retraction of the valve stem causes the valve core to move upward, thereby increasing the flow cross-sectional area inside the valve. Electric regulating valves are typically also equipped with position feedback sensors, such as potentiometers or Hall effect sensors, to feed back the actual position of the valve stem to the control module, forming a closed-loop control. This allows the control module to continuously fine-tune the output signal based on the feedback signal until the valve stem reaches the target chilled water volume flow rate command. The corresponding precise opening.

[0164] In summary, the ground source heat pump coupled fresh air dehumidification system and method provided in this embodiment, through the coordinated linkage of the sensing module, control module and flow actuator, constructs a closed-loop optimization and self-diagnostic control system that takes into account mechanism transparency, logical causality and control stability.

[0165] First, addressing the problem that traditional control systems blindly rely on simple PID feedback for end temperature and humidity and cannot perceive the mass transfer limits inside the heat exchanger, this system comprehensively collects real-time operating parameters from both the air and water sides through a sensing module. Furthermore, the control module performs rigorous calculations of the underlying fluid and heat transfer parameters based on thermodynamic principles and the Antoine equation, accurately extracting key physical quantities such as dry air mass flow rate, inlet and outlet air enthalpy, dehumidification contact coefficient, and moisture extraction coefficient. This lays a solid physical calculation foundation for the operation of subsequent advanced control models.

[0166] Secondly, to address the issues of sensible heat overflow and insufficient latent heat dehumidification that are common in traditional control systems, the system encapsulates a cold air coupling model and a latent heat conversion model. The cold air coupling model is based on the efficiency-number of heat transfer units ( The theory uses the mapping relationship between wind speed ratio and temperature difference ratio as a characterization of heat transfer impedance matching degree; the latent heat conversion model quantifies the actual proportion of cold energy converted into pure dehumidification latent heat. When the above-mentioned cold air coupling degree or latent heat conversion efficiency falls to the preset control lower limit, the control module actively sends an opening limit command to the electric regulating valve, forcibly driving the valve core to move downward to limit the cold water flow area, thereby stopping the loss and suppressing the ineffective cold energy output under inefficient operating conditions.

[0167] Furthermore, to address the causal inversion logic flaw caused by using the air outlet status of the surface cooler to infer the external load in existing technologies (i.e., when the system's dehumidification capacity decreases due to a fault, it is mistakenly judged as a decrease in external load), the supply-demand two-dimensional mapping model directly extracts the difference between the absolute moisture content of the incoming air and the preset target absolute moisture content of the supply air. Combined with the absolute temperature difference ratio, it extracts the load bias factor, accurately decoupling the true external load demand that is not affected by the current system processing results. At the same time, it combines the geometric mean of the cold air coupling degree and the latent heat conversion efficiency to generate an internal operating efficiency that comprehensively reflects the heat exchange potential of the system, achieving an objective and accurate two-dimensional mapping between the supply and demand sides.

[0168] Furthermore, to address the potential for control divergence caused by sensor zero-point drift, drainage pipe blockage, or condensate splashing leading to data distortion at the engineering site, the dehumidification reliability model introduces a verification mechanism based on mass conservation. Within a discrete sliding time window, the model compares the theoretical average desiccation flow rate determined by the difference between dry air flow rate and absolute moisture content with the measured average drainage flow rate measured by the condensate flow meter. Dehumidification reliability is calculated through deviation penalty. When the dehumidification reliability drops to the zero-point threshold, the system issues a position-holding and anti-shake command. This position-holding and anti-shake command is given the highest system control priority within the control module, which can forcibly shield and cover valve position displacement commands issued based on other validity indicators, cut off the actuator's response to the dynamic adjustment electrical signal, and fix the current valve position with the help of an internal self-locking mechanism. This completely avoids the problem of mutual exclusion of multi-dimensional control commands under extreme abnormal operating conditions, which can lead to actuator deadlock or frequent oscillation.

[0169] Finally, in the target flow optimization calculation stage, to address the technical challenge that directly using the dynamic actual flow in the closed loop as the multiplication benchmark can easily lead to positive feedback divergence and integral saturation, the chilled water real-time flow optimization model uses the preset rated chilled water volume flow rate as a stable open-loop anchor point benchmark. Combining the external load demand and internal operating efficiency after dehumidification reliability weighting, it calculates the flow scaling factor without the risk of self-excitation amplification, generates an accurate target chilled water volume flow rate command, and drives the transmission component of the electric regulating valve to perform smooth flow expansion or contraction actions.

[0170] By organically linking and logically constraining the aforementioned sensors, thermodynamic calculation models, reliability error prevention mechanisms, and open-loop anchor point optimization algorithms, this invention integrates external real load perception, internal energy conversion assessment, physical process quality conservation self-diagnosis, high-priority position preservation and anti-shaking, and non-divergent dynamic optimization. It not only overcomes the shortcomings of traditional PID control, such as easy divergence, easy oscillation, and poor adaptability to variable fresh air loads, but also endows the system with a high degree of self-diagnosis and safety resistance when the underlying data is distorted, effectively ensuring the high energy efficiency, high precision, and high robustness of the overall operation of the ground source heat pump coupled fresh air dehumidification system.

[0171] A dehumidification method for a ground source heat pump coupled with fresh air, applied to the aforementioned ground source heat pump coupled with fresh air dehumidification system, includes the following steps:

[0172] S1: Real-time acquisition of air and water side operating parameters via the sensing module and transmission to the control module;

[0173] S2: When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, it activates the internal cold air coupling model and latent heat conversion model to calculate and obtain the cold air coupling degree and latent heat conversion effectiveness.

[0174] S3: The control module activates the internal supply and demand two-dimensional mapping model and dehumidification reliability model to calculate and obtain the external load demand, internal operating effectiveness, and dehumidification reliability.

[0175] S4: The control module activates the internal real-time chilled water flow optimization model, extracts the external load demand, internal operating efficiency and dehumidification reliability, and calculates and generates the target chilled water volume flow command.

[0176] S5: The electric regulating valve receives the target chilled water volume flow command, executes the corresponding valve core displacement action, and adjusts the flow area of ​​the chilled water entering the surface cooler.

[0177] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of the present invention is defined by the appended claims and their equivalents.

Claims

1. A ground source heat pump coupled with fresh air dehumidification system, characterized in that: include: Sensing Module: Used to collect air-side and water-side operating parameters, including an inlet water temperature sensor installed on the chilled water inlet pipe section of the fresh air dehumidifier to obtain the real-time chilled water inlet temperature; a frontal anemometer installed on the windward side of the surface cooler to obtain the real-time frontal wind speed; a condensate flow meter installed on the drain riser of the water tray to obtain the instantaneous drainage flow rate; inlet air temperature, humidity, and dew point sensors installed on the intake section to obtain the inlet air dry-bulb temperature, inlet air relative humidity, and inlet air dew point temperature; outlet air temperature and humidity sensors installed on the supply air section to obtain the outlet air dry-bulb temperature and outlet air relative humidity; and a surface temperature sensor installed on the coil surface to obtain the coil surface dry-bulb temperature. And a chilled water flow meter installed in the return water pipe section to obtain the real-time chilled water volume flow rate; Control module: interconnected with the sensing module via a communication bus, internally encapsulating a cold air coupling model, a latent heat conversion model, a supply-demand two-dimensional mapping model, a dehumidification confidence model, and a chilled water real-time flow optimization model; the control module is configured to generate source-load synergy and dehumidification confidence based on the acquired operating parameters, and output a target chilled water volume flow rate command; Flow actuator: includes an electric regulating valve connected in series in the return water pipe section, the pipe of which is connected to the ground source heat pump host manifold to form a cold water circulation loop; the electric regulating valve is configured to receive the target chilled water volume flow command and perform the corresponding valve core displacement action.

2. The ground source heat pump coupled fresh air dehumidification system according to claim 1, characterized in that: When the control module determines that the inlet dry-bulb temperature is greater than the outlet dry-bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, it extracts fluid and heat exchange conversion parameters. The feature extraction logic is as follows: Based on the preset dry air density constant, the effective windward cross-sectional area constant of the surface cooler, and the real-time oncoming wind speed, the dry air mass flow rate is calculated and obtained. Based on the inlet dry-bulb temperature and inlet relative humidity, combined with the calculation of water vapor saturation partial pressure and molar mass ratio conversion, the absolute moisture content of the inlet air is calculated and obtained. Based on the outlet dry-bulb temperature and outlet relative humidity, combined with the calculation of water vapor saturation partial pressure and molar mass ratio conversion, the absolute moisture content of the outlet air is calculated and obtained. Based on the isobaric specific heat capacity constant of dry air and water vapor and the latent heat of vaporization of water, combined with the dry-bulb temperature and absolute moisture content of the corresponding measuring points, the specific enthalpy of the inlet air and the specific enthalpy of the outlet air are calculated and obtained respectively, and the specific enthalpy of saturated air at the average temperature of the coil surface is calculated based on the dry-bulb temperature of the coil surface. The difference between the enthalpy of the inlet air and the enthalpy of the outlet air is used as the first calculation item, and the difference between the enthalpy of the inlet air and the enthalpy of the saturated air on the coil surface is used as the second calculation item. The dehumidification contact coefficient is calculated by the proportional relationship between the first calculation item and the second calculation item. Using the first calculation term as the numerator and the sensible heat change obtained by multiplying the temperature difference between the inlet and outlet dry bulbs by the constant pressure specific heat capacity constant as the denominator, the moisture extraction coefficient is calculated. In the second calculation term of the dehumidification contact coefficient and the denominator of the dehumidification coefficient, a preset minimum bias constant is simultaneously substituted into the summation operation.

3. The ground source heat pump coupled fresh air dehumidification system according to claim 2, characterized in that: The data processing logic for the cold air coupling model and the latent heat conversion model is as follows: The cold air coupling model uses the ratio of the real-time oncoming wind speed to the preset rated oncoming wind speed as the first input, and the ratio of the temperature difference between the inlet dry bulb temperature and the real-time chilled water inlet temperature to the preset rated heat transfer temperature difference as the second input. It calculates the deviation of the ratio of the first input to the second input relative to the preset ratio constant, and calculates the output cold air coupling degree based on the deviation through a nonlinear decay function. The latent heat conversion model performs algebraic constraint mapping calculation on the dehumidification coefficient to extract the latent heat share weight; the latent heat share weight is multiplied and weighted with the dehumidification contact coefficient to calculate and output the latent heat conversion effectiveness.

4. A ground source heat pump coupled fresh air dehumidification system according to claim 3, characterized in that: The control module is configured to perform the following adjustment steps based on the cold air coupling degree and latent heat conversion efficiency: S11: The control module reads the extracted values ​​of cold air coupling degree and latent heat conversion efficiency; S12: When it is determined that the cold air coupling degree or latent heat conversion efficiency has fallen to the preset control lower limit threshold, the control module sends an opening limit command to the electric regulating valve. S13: After receiving the opening limit command, the internal servo motor of the electric regulating valve drives the valve core to move downward and enter the valve position limit state, reducing the internal cold water flow area.

5. A ground source heat pump coupled fresh air dehumidification system according to claim 4, characterized in that: The feature extraction logic of the supply-demand two-dimensional mapping model and the dehumidification reliability model is as follows: The supply and demand two-dimensional mapping model converts the inlet air dew point temperature and the reference inlet air dew point temperature into absolute temperatures, calculates the ratio of the converted inlet air dew point temperature to the reference inlet air dew point temperature, multiplies the ratio by the ratio of the difference between the absolute moisture content of the inlet air and the target absolute moisture content to the difference between the rated moisture content, extracts the load bias factor, performs a bounded mapping operation on the load bias factor through an algebraic smoothing activation function, outputs the external load demand degree, and calculates the square root of the product of the cold air coupling degree and the latent heat conversion effectiveness to output the internal operating effectiveness. The dehumidification reliability model calculates the theoretical average moisture extraction flow rate, determined by the difference between the dry air mass flow rate and the absolute moisture content of the inlet and outlet air, within a preset discrete sliding time window. It also calculates the measured average drainage flow rate collected by the condensate flow meter. The deviation between the theoretical average moisture extraction flow rate and the measured average drainage flow rate is reciprocally decayed using a fractional calculation logic with bidirectional symmetry to output the dehumidification reliability.

6. A ground source heat pump coupled fresh air dehumidification system according to claim 5, characterized in that: The control module is configured to perform the following adjustment steps based on the dehumidification reliability: S21: The control module reads the calculated dehumidification reliability; S22: When it is determined that the dehumidification reliability drops to the preset zero threshold range, the control module sends a position-keeping and anti-shaking command to the electric regulating valve. The position-keeping and anti-shaking command has the highest control priority and forcibly blocks and covers the valve core displacement command generated by the system based on other validity indicators. S23: After receiving the position-keeping and anti-shake command, the actuator of the electric regulating valve cuts off the response to the dynamic regulation electrical signal and performs the position-keeping action to fix the valve core displacement at the current moment with the internal self-locking mechanism.

7. A ground source heat pump coupled fresh air dehumidification system according to claim 6, characterized in that: The data processing logic of the real-time cold water flow optimization model is as follows: The real-time chilled water flow optimization model uses the preset rated chilled water volumetric flow rate as the benchmark value to extract the external load demand, internal operating efficiency, and dehumidification reliability. The product of the dehumidification reliability and the external load demand is calculated as the first adjustment weight, and the product of the dehumidification reliability and the internal operational effectiveness is calculated as the second adjustment weight. Based on the numerator containing the first adjustment weight and the denominator containing the second adjustment weight, the flow scaling factor is calculated and obtained. The preset rated chilled water volumetric flow rate is multiplied by the flow rate scaling factor to output the target chilled water volumetric flow rate command normally. When the dehumidification confidence approaches the preset zero-point threshold, the flow rate scaling factor approaches one, so that the value of the generated target chilled water volumetric flow rate command is equal to the preset rated chilled water volumetric flow rate.

8. A ground source heat pump coupled fresh air dehumidification system according to claim 7, characterized in that: The control module is configured to perform the following adjustment steps based on the target chilled water volume flow rate command: S31: The control module reads the value of the target chilled water volume flow rate command generated by the calculation; S32: When it is determined that the external load demand is greater than the internal operating efficiency, the control module outputs a positive current amplification signal to the electric regulating valve; S33: After receiving the positive flow amplification signal, the electric regulating valve drives the valve stem to perform an upward retraction action through its internal transmission component; S34: The retraction displacement of the valve stem expands the annular cross-sectional area of ​​the cold water flow, adjusting the actual chilled water flow rate through the surface cooler to the mechanical opening corresponding to the target chilled water volume flow rate command.

9. A dehumidification method for a ground source heat pump coupled with fresh air, wherein the method is applied to the ground source heat pump coupled with fresh air dehumidification system as described in claim 8, characterized in that: Includes the following steps: S1: The sensing module collects the air and water side operating parameters in real time and transmits them to the control module; S2: When the control module determines that the inlet dry bulb temperature is greater than the outlet dry bulb temperature and the absolute moisture content of the inlet air is greater than the absolute moisture content of the outlet air, it activates the internal cold air coupling model and latent heat conversion model to calculate and obtain the cold air coupling degree and latent heat conversion efficiency. S3: The control module activates the internal supply and demand two-dimensional mapping model and dehumidification reliability model to calculate and obtain the external load demand, internal operating effectiveness, and dehumidification reliability. S4: The control module activates the internal real-time chilled water flow optimization model, extracts the external load demand, internal operating efficiency and dehumidification reliability, and calculates and generates the target chilled water volume flow command. S5: The electric regulating valve receives the target chilled water volume flow command, executes the corresponding valve core displacement action, and adjusts the flow area of ​​the chilled water entering the surface cooler.

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