A control method and system for a refrigeration appliance

Abstract

The application discloses a kind of control method and system of refrigeration equipment, it is related to refrigeration equipment control technical field.The control method of the refrigeration equipment, by obtaining the air heat exchange time series data of setting refrigeration equipment, compression sound pressure signal data, condensation state time series data;Based on the air heat exchange time series data of setting refrigeration equipment, condensation state time series data, respectively analyze the heat exchange dew point control characteristic value of setting refrigeration equipment, condensation dew point control characteristic value;Based on the sound pressure dew point mapping model of pre-training, and in combination with the compression sound pressure signal data of setting refrigeration equipment, analyze the sound pressure dew point control characteristic value of setting refrigeration equipment, the present application is based on heat exchange dew point control characteristic value, condensation dew point control characteristic value, sound pressure dew point control characteristic value is carried out joint dew point control to setting refrigeration equipment, to be able to fully express the influence law of refrigeration equipment in different links to dew point temperature, to guarantee the precision of dew point control, to significantly improve the quality of compressed air.

Description

Technical Field

[0001] This invention relates to the field of refrigeration equipment control technology, specifically to a control method and system for refrigeration equipment. Background Technology

[0002] Refrigeration equipment is widely used in industrial production and civilian applications to regulate the temperature and humidity of air, liquids, or process media. Among various refrigeration equipment, the refrigerated air dryer is one of the most widely used devices. Its working principle is to use a refrigeration cycle to cool the incoming compressed air to near the dew point temperature, causing the water vapor in the air to condense and be discharged through the drainage system, thereby reducing the moisture content of the compressed air.

[0003] During the operation of a refrigerated air dryer, the dew point temperature of the outlet air is an important indicator for measuring the air drying effect. The lower the dew point temperature, the more fully the water vapor in the air is condensed, and the lower the moisture content of the compressed air, which can better meet the process scenarios with high requirements for gas dryness. Conversely, when the dew point temperature is too high, it means that there is more residual moisture in the air, which may lead to pipeline corrosion, etc. Therefore, it is necessary to accurately control the outlet dew point temperature during the operation of the refrigeration equipment.

[0004] Existing technologies, such as the control method, control device, and refrigeration equipment disclosed in patent application CN120538226A, are applied to the control module in a refrigeration equipment. The method includes: acquiring target multidimensional data collected by the data acquisition module at the data acquisition time; inputting the target multidimensional data into a temperature prediction model to obtain a predicted internal temperature inside the refrigeration equipment; acquiring the target internal temperature detected by the temperature detection module at the data acquisition time; correcting the target internal temperature according to the predicted internal temperature to obtain a corrected internal temperature; and adjusting the working state of the refrigeration equipment based on the corrected internal temperature. The method provided by this invention not only improves the control accuracy of the refrigeration equipment but also adapts to different changes in the refrigeration equipment and reduces the accumulation of errors caused by multidimensional data.

[0005] Based on the above findings, the limitations of existing technologies include at least the following problems: Existing technologies lack joint analysis of the air heat exchange process, condensation drainage process, and compressor sound pressure state of refrigeration equipment. This easily leads to one-sided dew point control, making it difficult to accurately reflect the true dryness level of the outlet air. For example, when heat exchange efficiency is insufficient, the evaporator surface cannot fully drive water vapor condensation, resulting in increased residual moisture in the air and a higher outlet dew point temperature. Furthermore, when condensate drainage is poor, water accumulation or liquid film coverage increases heat transfer resistance and may even trigger secondary evaporation, thus worsening the dew point control effect. Simultaneously, compressor sound pressure fluctuations couple to the evaporator heat exchange and condensation processes, causing irregular fluctuations in dew point temperature. There is a high degree of coupling between heat exchange, condensation, and sound pressure state, but existing technologies have failed to establish joint control, making dew point control prone to delays or deviations, and failing to meet the demand for efficient and stable compressed air drying. Summary of the Invention

[0006] To address the shortcomings of existing technologies, this invention provides a control method and system for refrigeration equipment, which solves the problems of lack of cross-stage linkage control, leading to inaccurate dew point control and unstable drying effect.

[0007] To achieve the above objectives, the present invention provides the following technical solution: a control method for a refrigeration device, comprising the following steps: acquiring air heat exchange time-series data, compression sound pressure signal data, and condensation state time-series data of the refrigeration device; analyzing the heat exchange dew point control characteristic value and the condensation dew point control characteristic value of the refrigeration device based on the air heat exchange time-series data and the condensation state time-series data of the refrigeration device; analyzing the sound pressure dew point control characteristic value of the refrigeration device based on a pre-trained sound pressure dew point mapping model and in conjunction with the compression sound pressure signal data of the refrigeration device; and performing joint dew point control on the refrigeration device based on the heat exchange dew point control characteristic value, the condensation dew point control characteristic value, and the sound pressure dew point control characteristic value.

[0008] Furthermore, the air heat exchange time series data includes the drying load factor, flow velocity disturbance value, evaporation surface temperature difference value, evaporation heat exchange driving force value, evaporation airflow resistance factor, and outlet air saturation deviation value at each time point. The specific steps for analyzing and setting the heat exchange dew point regulation characteristic value of the refrigeration equipment are as follows: Based on the set air heat exchange time series data of the refrigeration equipment, analyze and set the efficiency dew point adjustment time series characteristic set of the refrigeration equipment, including the air drying efficiency characteristic value and evaporation heat exchange efficiency characteristic value at each time point; based on the set efficiency dew point adjustment time series characteristic set of the refrigeration equipment, analyze the heat exchange dew point driving characteristic value at the corresponding time point; based on the set heat exchange dew point driving characteristic value of the refrigeration equipment at each time point, analyze and set the heat exchange dew point regulation characteristic value of the refrigeration equipment.

[0009] Furthermore, the specific steps for analyzing the performance dew point adjustment time sequence characteristic set of the refrigeration equipment are as follows: Based on the drying load factor, flow rate disturbance value, and outlet air saturation deviation value of the refrigeration equipment at each time point, analyze the air drying performance characteristic value at the corresponding time point; Based on the evaporation surface temperature difference value, evaporation heat transfer driving force value, and evaporation airflow resistance factor of the refrigeration equipment at each time point, analyze the evaporation heat transfer performance characteristic value at the corresponding time point.

[0010] Furthermore, the condensation state time-series data includes the condensation precipitation rate, water accumulation height, condensation flow rate, condensation latent heat release rate, condensate film thermal resistance, and condensation phase change equilibrium value at each time point. The specific steps for analyzing and setting the condensation dew point regulation characteristic value of the refrigeration equipment are as follows: Based on the condensation state time-series data of the refrigeration equipment, analyze and set the condensation dew point adjustment time-series characteristic set of the refrigeration equipment, including the condensation release characteristic value and condensation stagnation characteristic value at each time point; based on the condensation dew point adjustment time-series characteristic set of the refrigeration equipment, analyze and set the condensation dew point regulation characteristic value of the refrigeration equipment.

[0011] Furthermore, the specific steps for analyzing the timing characteristic set of the condensation dew point adjustment of the refrigeration equipment are as follows: Based on the condensation precipitation rate, condensation flow rate, and condensation latent heat release rate of the refrigeration equipment at each time point, analyze the condensation release characteristic value at the corresponding time point; Based on the water accumulation height, condensate film thermal resistance, and condensation phase change equilibrium value of the refrigeration equipment at each time point, analyze the condensation stagnation characteristic value at the corresponding time point.

[0012] Further, the specific steps for analyzing and setting the sound pressure dew point control characteristics of the refrigeration equipment are as follows: input the compressed sound pressure signal data of the refrigeration equipment into the pre-trained sound pressure dew point mapping model, analyze the sound pressure mapping characteristic set of the refrigeration equipment, including sound pressure impact intensity characteristic value, harmonic leakage fluctuation characteristic value, and frequency band offset equalization characteristic value; based on the sound pressure mapping characteristic set of the refrigeration equipment, analyze the sound pressure dew point control characteristics of the refrigeration equipment.

[0013] Furthermore, the compressed sound pressure signal data specifically refers to the compressed sound pressure amplitude at each time point, and the sound pressure dew point mapping model includes an input partitioning layer, a sound pressure coding layer, a sound pressure time-varying layer, and an output layer.

[0014] Further, the specific steps for analyzing the sound pressure mapping feature set of the set refrigeration equipment are as follows: In the input partitioning layer of the sound pressure dew point mapping model, the compressed sound pressure signal data of the set refrigeration equipment is received and divided into several frames of sound pressure signals of the set refrigeration equipment; in the sound pressure coding layer of the sound pressure dew point mapping model, the sound pressure feature vector of the corresponding frame is extracted based on the several frames of sound pressure signals of the set refrigeration equipment; in the sound pressure time-varying layer of the sound pressure mapping model, the sound pressure mapping time sequence feature vector of the set refrigeration equipment is extracted based on the sound pressure feature vector of each frame of the set refrigeration equipment; in the output layer of the sound pressure dew point mapping model, the sound pressure mapping feature set of the set refrigeration equipment is output based on the sound pressure mapping time sequence feature vector of the set refrigeration equipment.

[0015] Furthermore, the specific steps for joint dew point control of the set refrigeration equipment based on the heat exchange dew point control characteristic value, condensation dew point control characteristic value, and sound pressure dew point control characteristic value are as follows: The heat exchange dew point control characteristic value, condensation dew point control characteristic value, and sound pressure dew point control characteristic value of the set refrigeration equipment are normalized; the normalized heat exchange dew point control characteristic value, condensation dew point control characteristic value, and sound pressure dew point control characteristic value of the set refrigeration equipment are compared with several preset dew point adjustment intervals for judgment and analysis; based on the judgment and analysis results, corresponding dew point control measures are taken for the set refrigeration equipment.

[0016] A control system for a refrigeration device includes: a data acquisition module for acquiring air heat exchange time-series data, compression sound pressure signal data, and condensation state time-series data of the refrigeration device; a heat exchange / condensation / dew point control analysis module for analyzing the heat exchange dew point control characteristic value and the condensation dew point control characteristic value of the refrigeration device based on the air heat exchange time-series data and the condensation state time-series data of the refrigeration device, respectively; a sound pressure / dew point control analysis module for analyzing the sound pressure / dew point control characteristic value of the refrigeration device based on a pre-trained sound pressure / dew point mapping model and combined with the compression sound pressure signal data of the refrigeration device; and a combined dew point control module for performing combined dew point control on the refrigeration device based on the heat exchange dew point control characteristic value, the condensation dew point control characteristic value, and the sound pressure / dew point control characteristic value.

[0017] The present invention has the following beneficial effects:

[0018] (1) The control method of the refrigeration equipment introduces air heat exchange time sequence data, condensation state time sequence data and compression sound pressure signal data, and analyzes and obtains the corresponding characteristic values. Thus, under the same control logic, it can realize the comprehensive reflection of the evaporator heat exchange capacity, condensation drainage efficiency and compressor operating status. The above characteristic values ​​complement and restrict each other, and can comprehensively describe the influence law of the refrigeration equipment on the dew point temperature in different links. Through interval judgment, joint control is realized to ensure the accuracy of dew point control. At the same time, it can make the drying effect of the outlet air more stable and reliable, thereby significantly improving the quality of compressed air and meeting the continuous dehumidification needs in high humidity environments.

[0019] (2) The control method of the refrigeration equipment introduces the compression sound pressure signal data of the refrigeration equipment and constructs a sound pressure dew point mapping model to perform in-depth analysis of the compression sound pressure signal data, thereby transforming acoustic information into features that reflect dew point changes. The model preprocesses and frames the original sound pressure signal through the input partitioning layer, extracts the corresponding sound pressure features in the sound pressure coding layer, and analyzes its temporal relationship in the sound pressure time-varying layer, thereby obtaining sound pressure mapping features that can reflect the compressor operating status and refrigerant circulation characteristics. Based on this, the sound pressure dew point regulation feature value is analyzed, thereby realizing the correlation between acoustic signal and outlet dew point temperature. In the process of dew point control, the influence of compressor operation fluctuation on dew point can be reflected, and the overall control accuracy is improved.

[0020] (3) The control method of the refrigeration equipment obtains the air heat exchange time sequence data of the refrigeration equipment and analyzes the heat exchange dew point regulation characteristic value, thereby reflecting the correspondence between the heat exchange performance of the evaporator and the outlet dew point temperature. It comprehensively considers the heat exchange efficiency of air and refrigerant in the evaporator and converts it into heat exchange dew point regulation characteristic value, thereby characterizing the regulation effect of the evaporator on the dew point temperature under different working conditions, so that the dew point control can be dynamically adjusted based on the overall heat exchange performance of the evaporator, thereby improving the accuracy of control and ensuring that the compressed air can maintain good drying quality under different load conditions.

[0021] (4) The control system of the refrigeration equipment achieves precise adjustment of dew point temperature through collaborative analysis between modules. The data acquisition module ensures the synchronous acquisition of multi-source information such as air heat exchange, condensation state and sound pressure signal. Each analysis module converts the corresponding data into characteristic values ​​that can be directly used for control, ensuring that the key links affecting the dew point are reflected by corresponding characteristics. The joint dew point control module coordinates on this basis to achieve balanced adjustment between different characteristic values, thereby improving the stability of dew point control and ensuring that compressed air maintains high dryness quality under continuous working conditions.

[0022] Of course, any product implementing this invention does not necessarily need to achieve all of the advantages described above at the same time. Attached Figure Description

[0023] Figure 1 This is a flowchart of a control method for a refrigeration device according to the present invention.

[0024] Figure 2 This is a flowchart illustrating the specific steps involved in analyzing and setting the heat exchange dew point regulation characteristic value of a refrigeration equipment in a control method for a refrigeration equipment according to the present invention.

[0025] Figure 3 This is a schematic diagram of the timing feature set data for setting the efficiency dew point adjustment of a refrigeration device in a control method for a refrigeration device according to the present invention.

[0026] Figure 4 This is a block diagram of a control system for a refrigeration device according to the present invention. Detailed Implementation

[0027] Please see Figure 1 This invention provides a technical solution: a control method for a refrigeration device, comprising the following steps: within a set period (e.g., 3 seconds), acquiring air heat exchange time-series data, compression sound pressure signal data, and condensation state time-series data of a set refrigeration device (e.g., a refrigerated air dryer); based on the air heat exchange time-series data and condensation state time-series data of the set refrigeration device, analyzing the heat exchange dew point control characteristic value and the condensation dew point control characteristic value of the set refrigeration device respectively; based on a pre-trained sound pressure dew point mapping model, and combined with the compression sound pressure signal data of the set refrigeration device, analyzing the sound pressure dew point control characteristic value of the set refrigeration device; and performing joint dew point control on the set refrigeration device based on the heat exchange dew point control characteristic value, the condensation dew point control characteristic value, and the sound pressure dew point control characteristic value.

[0028] The specific steps for joint dew point control of a set refrigeration equipment based on heat exchange dew point control characteristic values, condensation dew point control characteristic values, and sound pressure dew point control characteristic values ​​are as follows: The heat exchange dew point control characteristic values, condensation dew point control characteristic values, and sound pressure dew point control characteristic values ​​of the set refrigeration equipment are normalized (mapped to between 0 and 1); the normalized heat exchange dew point control characteristic values, condensation dew point control characteristic values, and sound pressure dew point control characteristic values ​​of the set refrigeration equipment are compared with several preset dew point adjustment intervals (each set of ash conveying dew point intervals includes one heat exchange dew point control interval, one condensation dew point control interval, and one sound pressure dew point control interval, and each set of dew point adjustment intervals corresponds to one dew point control measure).

[0029] Based on the judgment and analysis results, corresponding dew point control measures are taken for the set refrigeration equipment, specifically as follows:

[0030] When the normalized dew point control characteristic values ​​of the heat exchange dew point control characteristic value, condensation dew point control characteristic value, and sound pressure dew point control characteristic value of the set refrigeration equipment are within the preset dew point adjustment range, the corresponding dew point control measures are applied to the set refrigeration equipment, including but not limited to the following examples:

[0031] Interval Group 1 (High-efficiency heat exchange, sufficient condensation, ideal sound pressure):

[0032] Heat exchange dew point control range: 0.7-1.0 (indicating excellent heat exchange performance of the evaporator and strong dehumidification driving capability);

[0033] Condensation dew point control range: 0.7-1.0 (indicating sufficient condensation and smooth drainage);

[0034] Sound pressure dew point control range: 0.7-1.0 (indicating that the compressor is operating at its best and the refrigerant circulation is highly efficient);

[0035] Corresponding dew point control measures: When the refrigerated air dryer is in optimal operating condition, the outlet dew point temperature is extremely low and stable, and an energy-saving maintenance strategy can be implemented: maintain all current operating parameters, and even moderately reduce the condenser fan speed or compressor frequency to the minimum requirement to maintain this state, so as to reduce energy consumption and ensure that the dew point temperature is stable at the target value.

[0036] Zone 2 (High-efficiency heat exchange, insufficient condensation, good condition):

[0037] Heat exchange dew point control range: 0.7-1.0 (indicating good heat exchange performance of the evaporator);

[0038] Condensation dew point control range: 0.0-0.3 (indicating poor condensation effect or potential blockage in drainage);

[0039] Sound pressure dew point control range: 0.6-0.9 (indicating normal compressor operation);

[0040] Corresponding dew point control measures: The evaporator is capable of providing cooling capacity at lower temperatures, but the condenser-side problem limits the reduction of the dew point. Implement condenser-side optimization strategies: First, check the drain function, increase the drain frequency or duration, and increase the condenser fan speed or start auxiliary cooling to enhance the condensation effect, reduce the condensation pressure, thereby improving the overall cooling efficiency and driving the dew point temperature down.

[0041] Interval Group 3 (Poor heat exchange, insufficient condensation, abnormal sound pressure):

[0042] Heat exchange dew point control range: 0.0-0.4 (indicates a decrease in evaporator heat exchange performance, possibly due to frost or fouling).

[0043] Condensation dew point control range: 0.7-1.0 (indicating normal operation of the condenser side);

[0044] Sound pressure dew point control range: 0.0-0.4 (indicates that the compressor load is light or there may be refrigerant leakage, resulting in abnormal sound pressure characteristics);

[0045] Corresponding dew point control measures: The condenser side is normal, but the evaporator heat exchange efficiency and compressor status are poor, and the outlet dew point temperature rises. Implement hot bypass control and defrosting strategies: The hot gas bypass valve can be activated to introduce some high-temperature refrigerant into the evaporator inlet to prevent further freezing and defrosting; at the same time, check the refrigerant charge and compressor operating current to diagnose whether there is a leak or mechanical failure, and perform maintenance and adjustment accordingly.

[0046] Interval Group 4 (Insufficient heat exchange, insufficient condensation, moderate sound pressure):

[0047] Heat exchange dew point control range: 0.2-0.5 (indicating low evaporator heat exchange efficiency);

[0048] Condensation dew point control range: 0.2-0.5 (indicating moderate condensation effect);

[0049] Sound pressure dew point control range: 0.4-0.6 (indicating that the compressor is operating at a critical level);

[0050] Corresponding dew point control measures: The overall performance of the refrigerated air dryer is below average, and the dew point temperature control is not ideal. Implement a system balancing adjustment strategy: fine-tune the opening of the thermal expansion valve and optimize the refrigerant flow; synchronously adjust the operating frequency of the condenser fan and compressor so that the dew point temperature gradually returns to the set range.

[0051] Interval group 5 (overall poor performance):

[0052] Heat exchange dew point control range: 0.0-0.2 (indicating severe loss of evaporator heat exchange efficiency);

[0053] Condensation dew point control range: 0.0-0.2 (indicating severely insufficient condensation);

[0054] Sound pressure dew point control range: 0.0-0.2 (indicating abnormal compressor operation);

[0055] Corresponding dew point control measures: If the performance of the refrigerated air dryer is severely deteriorated and the outlet dew point temperature far exceeds the set value, implement a shutdown maintenance and comprehensive diagnostic strategy: Immediately activate the alarm and recommend shutdown for inspection. The inspection items include, but are not limited to: whether the evaporator is severely iced or contaminated, whether the condenser is blocked, whether the drainer is completely ineffective, whether the refrigerant is seriously leaking, and whether the compressor is malfunctioning. The refrigerated air dryer can only be restarted after thorough maintenance.

[0056] Specifically, such as Figure 2 As shown, the air heat exchange time series data includes the drying load factor, flow velocity disturbance value, evaporation surface temperature difference value, evaporation heat exchange driving force value, evaporation airflow resistance factor, and outlet air saturation deviation value at each time point. The specific steps for analyzing and setting the heat exchange dew point regulation characteristic value of the refrigeration equipment are as follows: Based on the set air heat exchange time series data of the refrigeration equipment, analyze and set the efficiency dew point adjustment time series characteristic set of the refrigeration equipment, including the air drying efficiency characteristic value and evaporation heat exchange efficiency characteristic value at each time point; based on the set efficiency dew point adjustment time series characteristic set of the refrigeration equipment, analyze the heat exchange dew point driving characteristics at the corresponding time points. The characteristic value (used to characterize the driving ability of the refrigerated air dryer to control the outlet dew point temperature of compressed air through heat exchange and dehumidification at a given moment; the larger the value, the better the air drying effect and the evaporator heat exchange performance are matched, the more fully the moisture in the air can be condensed and precipitated, and the lower the outlet dew point temperature); based on the heat exchange dew point driving characteristic value of the set refrigeration equipment at each time point, the heat exchange dew point control characteristic value of the set refrigeration equipment is analyzed. Specifically, the heat exchange dew point driving characteristic value of the set refrigeration equipment at each time point is processed by moving average to obtain the heat exchange dew point control characteristic value of the set refrigeration equipment.

[0057] The drying load factor is the combined load that the compressed air carries when it enters the refrigerated air dryer at a given moment, requiring cooling and dehumidification. It reflects the combined influence of air temperature, humidity, pressure, and flow rate on the refrigeration and drying process. It can be obtained by collecting the inlet temperature of compressed air by a temperature sensor, the inlet pressure by a pressure sensor, the inlet humidity by a humidity sensor, and the inlet flow rate by a flow meter. The inlet temperature, pressure, humidity, and flow rates are then standardized. The results of the standardization are weighted and used as the drying load factor. The larger the value, the stronger the heat exchange capacity of the evaporator is required to condense and precipitate water vapor. Otherwise, there will be too much residual moisture in the air and the outlet dew point temperature will rise.

[0058] The velocity disturbance value is the instantaneous deviation of air flow within the evaporator channel. It can be obtained by using wind speed sensors deployed at the evaporator inlet and outlet to acquire the inlet and outlet wind speed values, and then processing the deviation, i.e., |evaporator inlet wind speed value - evaporator outlet wind speed value| / evaporator inlet wind speed value. The result is used as the velocity disturbance value. The larger the value, the more significant the difference in air velocity between the inlet and outlet, resulting in insufficient heat exchange in some areas and incomplete water vapor condensation, thus causing the outlet dew point temperature to be higher.

[0059] The evaporator surface temperature difference is the instantaneous temperature difference between the air and the evaporator surface at a given moment. It reflects the cooling driving force of the evaporator on the compressed air. It can be obtained by collecting the air temperature value in the evaporator channel by an air temperature sensor and the evaporator surface temperature value by a temperature sensor installed on the evaporator wall. The difference between the two is processed (the absolute value is taken), and the result is used as the evaporator surface temperature difference value. The larger the value, the stronger the cooling effect of the evaporator surface on the air, the faster the air temperature can drop, and the lower the outlet dew point temperature.

[0060] The driving force of evaporative heat transfer is the effective temperature difference between the air and the refrigerant at the two ends of the evaporator at that moment. It is used to characterize the instantaneous heat transfer driving force of the evaporator. It can be obtained by placing temperature sensors at the air inlet of the evaporator to collect the air inlet temperature value, placing temperature sensors at the air outlet of the evaporator to collect the air outlet temperature value, and placing temperature sensors in the refrigerant evaporation section to collect the refrigerant evaporation temperature value. Based on the above temperature values, the evaporator inlet temperature difference (i.e., air inlet temperature value - refrigerant evaporation temperature value) and outlet temperature difference (i.e., air outlet temperature value - refrigerant evaporation temperature value) are calculated. (It should be noted that, in order to avoid calculation abnormalities caused by measurement errors, the absolute values ​​of the evaporator inlet temperature difference and outlet temperature difference can be used for processing.) The result is processed according to the logarithmic average temperature difference formula and used as the driving force of evaporative heat transfer. The larger the value, the stronger the heat transfer driving force between the air and the refrigerant in the evaporator, the more water vapor can be precipitated, and the lower the outlet dew point temperature.

[0061] The evaporative airflow resistance factor is a comprehensive resistance characteristic of air flowing within the evaporator channel. It can be obtained by installing pressure sensors at the evaporator inlet and outlet to acquire inlet and outlet pressure values, and temperature sensors at the same time to acquire inlet and outlet air temperatures. The differences between these values ​​are then processed to obtain evaporative pressure difference and evaporative temperature difference values, both taken as absolute values ​​and standardized. The standardized results are then weighted, with the standardized evaporative temperature difference value inverted during the weighting process, i.e., 1 / (1 + standardized evaporative temperature difference value). This result is used as the evaporative airflow resistance factor. A larger value indicates poor airflow and insufficient heat exchange between the air and the cold surface, resulting in incomplete dehumidification and an increased outlet dew point temperature.

[0062] The outlet air saturation deviation value is the difference between the actual humidity of the compressed air discharged from the evaporator outlet and its saturation state at the same temperature. It can be obtained by collecting the relative humidity value of the outlet compressed air by a humidity sensor and the temperature value of the outlet compressed air by a temperature sensor, and comparing it with the saturated relative humidity at that temperature (that is, under the saturated water vapor pressure condition corresponding to the outlet air temperature, the relative humidity of the air is taken as 100%, which is the theoretical saturation limit state of the air). The difference between the actual relative humidity and the saturated relative humidity of the outlet compressed air (take the absolute value) is obtained. The result is used as the outlet air saturation deviation value. The larger the value, the more moisture is condensed and removed, the drier the air is, and the lower the outlet dew point temperature.

[0063] The specific formula for calculating the heat exchange dew point drive characteristic value of a set refrigeration equipment at a certain time point is as follows: ;in, To set the heat exchange dew point driving characteristic value of the refrigeration equipment at a certain time point, To set the air drying efficiency characteristic value of the refrigeration equipment at a certain point in time, The drying efficiency adjustment coefficient is stored in the database. To set the characteristic value of the evaporative heat transfer efficiency of the refrigeration equipment at a certain point in time, The heat exchange efficiency adjustment coefficient is stored in the database. , These are the coordination adjustment coefficients stored in the database, and in this embodiment, the drying efficiency adjustment coefficients stored in the database. Heat exchange efficiency adjustment coefficient Coordination adjustment coefficient The values ​​were 0.426, 0.574, and 0.763, respectively.

[0064] The following is a specific implementation example for calculating the heat exchange dew point drive characteristic value of a set refrigeration equipment at a certain time point. The available data includes the air drying efficiency characteristic values ​​and evaporative heat exchange efficiency characteristic values ​​of the set refrigeration equipment at five randomly selected time points, as shown in Table 1 and... Figure 3 As shown:

[0065] Table 1. Example of data for setting the performance dew point adjustment time sequence characteristic set of refrigeration equipment.

[0066] Air drying efficiency characteristic value Evaporative heat transfer efficiency characteristic value Time point 1 0.782 0.812 Time point 2 0.763 0.784 Time point 3 0.794 0.806 Time point 4 0.803 0.793 Time point 5 0.748 0.773

[0067] Drying efficiency adjustment coefficients stored in the database The value is: 0.426;

[0068] Heat exchange efficiency adjustment coefficients stored in the database The value is: 0.574;

[0069] Coordination coefficients stored in the database The value is: 0.763;

[0070] Substituting the data from Table 1 and the aforementioned coefficients into the specific formula for calculating the heat exchange dew point drive characteristic value of the refrigeration equipment at a certain time point, we obtain:

[0071] The characteristic value of the heat exchange dew point drive of the refrigeration equipment at the first time point is set as follows: 0.426×0.782+0.574×0.812+ln(1+0.763×√(0.782×0.812))≈1.274;

[0072] The characteristic value of the heat exchange dew point driven by the refrigeration equipment at the second time point is set as follows: 0.426×0.763+0.574×0.784+ln(1+0.763×√(0.763×0.784))≈1.239;

[0073] The characteristic value of the heat exchange dew point driven by the refrigeration equipment at the third time point is set as follows: 0.426×0.794+0.574×0.806+ln(1+0.763×√(0.794×0.806))≈1.277;

[0074] The characteristic value of the heat exchange dew point drive at the fourth time point of the refrigeration equipment is set as follows: 0.426×0.803+0.574×0.793+ln(1+0.763×√(0.803×0.793))≈1.273;

[0075] The characteristic value of the heat exchange dew point drive at the fifth time point of the refrigeration equipment is set as follows: 0.426×0.748+0.574×0.773+ln(1+0.763×√(0.748×0.773))≈1.220.

[0076] The specific steps for analyzing the time-series characteristic set of the efficiency dew point adjustment of the refrigeration equipment are as follows: Based on the drying load factor, flow rate disturbance value, and outlet air saturation deviation value of the refrigeration equipment at each time point, analyze the air drying efficiency characteristic value at the corresponding time point. Specifically, the drying load factor, flow rate disturbance value, and outlet air saturation deviation value of the refrigeration equipment at each time point are standardized. The standardized results are then weighted (normalized to between 0 and 1). During the weighting process, the standardized drying load factor and flow rate disturbance value are inverted, such as 1 / (1+standardized drying load factor), to obtain the air drying efficiency characteristic value at the corresponding time point. This value is used to characterize the overall drying effect of compressed air at that time point. The larger the value, the more sufficient the air dehumidification and the lower the outlet dew point temperature.

[0077] Based on the evaporator surface temperature difference, evaporation heat transfer driving force, and evaporation airflow resistance factor of the refrigeration equipment at each time point, the characteristic value of evaporation heat transfer efficiency at the corresponding time point is analyzed. Specifically, the evaporator surface temperature difference, evaporation heat transfer driving force, and evaporation airflow resistance factor of the refrigeration equipment at each time point are standardized. The standardized results are then weighted (normalized to between 0 and 1). During this weighting process, the standardized evaporation airflow resistance factor is inverted, such as 1 / (1+standardized evaporation airflow resistance factor), to obtain the characteristic value of air drying efficiency at the corresponding time point. This value is used to characterize the overall heat transfer performance of the evaporator at that time point. The larger the value, the more sufficient the heat transfer, the more fully the air is cooled, and the lower the outlet dew point temperature.

[0078] In this implementation scheme, by decomposing and analyzing the air heat exchange time series data, the actual drying and heat exchange of compressed air in the evaporator can be comprehensively reflected, thereby reflecting the trend of dew point changes. For example, the drying load factor and flow velocity disturbance value combined with the outlet air saturation deviation value can intuitively reflect the water vapor load and flow state in the air entering the dryer, thereby analyzing the degree of air dehumidification at that moment. Furthermore, the air heat exchange time series data is standardized and weighted to generate air drying efficiency characteristic values ​​and evaporation heat exchange efficiency characteristic values, which are then summarized into heat exchange dew point driving characteristic values. This avoids the deviation caused by single-point temperature or humidity measurements and can maintain a continuous judgment basis when the operating conditions fluctuate, thus making the dew point control more stable and ensuring that the compressed air can maintain good drying quality under different loads.

[0079] Specifically, the condensation state time series data includes the condensation precipitation rate, water accumulation height, condensation flow rate, condensation latent heat release rate, condensate film thermal resistance, and condensation phase change equilibrium value at each time point. The specific steps for analyzing and setting the condensation dew point regulation characteristic value of the refrigeration equipment are as follows: Based on the condensation state time series data of the refrigeration equipment, analyze and set the condensation dew point adjustment time series characteristic set of the refrigeration equipment, including the condensation release characteristic value and condensation stagnation characteristic value at each time point.

[0080] Based on the time sequence feature set of the condensation dew point adjustment of the set refrigeration equipment, the condensation dew point control characteristic value of the set refrigeration equipment is analyzed. Specifically, the condensation release characteristic value and condensation stagnation characteristic value of the set refrigeration equipment at each time point are weighted. During the weighting process, the condensation stagnation characteristic value is inverted, i.e., 1 / (1+condensation stagnation characteristic value). The average value is then calculated based on the weighting results to obtain the condensation dew point control characteristic value of the set refrigeration equipment (used to characterize the comprehensive control effect of the refrigeration equipment on the outlet compressed air dew point temperature during the condensation and drainage process within the cycle. The larger the value, the more sufficient the condensation, the smoother the drainage, and the lower the outlet dew point temperature).

[0081] The condensation rate value is the amount of condensate that precipitates on the surface of the evaporator at that moment, which is used to characterize the intensity of water vapor condensation. It can be obtained by installing a miniature flow sensor on the condensate collection pipeline to collect the volumetric flow rate of condensate in real time and use it as the condensation rate value. The larger the value, the more condensate is precipitated on the surface of the evaporator per unit time, the lower the humidity in the air, and the lower the outlet dew point temperature.

[0082] The water accumulation height value is the liquid level height of the condensate collection tank at that moment, which is used to reflect the condensate retention. A capacitive or float-type liquid level sensor is installed in the condensate tank to collect the liquid level height in real time, and the result is used as the water accumulation height value. The larger the value, the more serious the condensate retention at the bottom of the evaporator. After the condensate covers the heat exchange surface, it will hinder the heat exchange process between air and refrigerant, resulting in an increase in the outlet dew point temperature.

[0083] The condensate flow rate is the flow rate of condensate discharged through the drain valve at that moment. It is used to characterize the efficiency of the drain operation. It can be measured in real time by installing an instantaneous flow sensor (such as a turbine or electromagnetic type) in the drain valve outlet pipe. The result is used as the condensate flow rate value. The larger the value, the more sufficient the condensate flow rate discharged by the drain valve is and the more efficient the operation is. The condensate will not stagnate and the outlet dew point temperature will be lower.

[0084] The latent heat release rate is the latent heat power released when water vapor in compressed air condenses into droplets on the evaporator surface. It is used to characterize the intensity of the condensation process at that moment. It can be obtained by setting a flow sensor in the condensate discharge pipeline to obtain the instantaneous flow rate of condensate, and converting it with the water density constant stored in the database to obtain the condensate mass flow rate (i.e., instantaneous flow rate × water density constant). Then, the latent heat of vaporization constant of water stored in the database is used for comprehensive analysis (condensate mass flow rate × latent heat of vaporization constant) to obtain the latent heat release rate value. The larger the value, the stronger the water vapor condensation, the more fully the air is dried, and the lower the outlet dew point temperature.

[0085] The condensate film thermal resistance is the resistance to heat transfer caused by the condensate film on the evaporator surface. It can be determined by placing heat flux sensors on the evaporator fins to collect the actual heat flux density in real time, and placing temperature sensors in the air and refrigerant channels to obtain the air-side temperature and refrigerant evaporation temperature. The difference between the two is the heat transfer temperature difference, which is then calculated as heat transfer temperature difference / actual heat flux density. The result is used as the condensate film thermal resistance value. The larger the value, the more severe the condensate film coverage, which hinders heat transfer, resulting in insufficient air cooling and an increased outlet dew point temperature.

[0086] The condensation phase change equilibrium value is the degree of balance between the condensate generation rate and the discharge rate at that moment. It is used to characterize the coordination between the condensation process and the drainage process. It can be obtained by reading the condensate mass flow rate and simultaneously acquiring the condensate discharge mass flow rate in real time from the flow sensor on the drainage pipeline, and then performing ratio processing, i.e., |condensate mass flow rate - discharge mass flow rate| / (condensate mass flow rate + discharge mass flow rate). The result is used as the condensation phase change equilibrium value. If this value is too large, it indicates that the difference between generation and discharge is significant, resulting in insufficient removal of water vapor in the air and an increase in the outlet dew point temperature.

[0087] The specific steps for analyzing the timing characteristic set of the condensation dew point adjustment of the refrigeration equipment are as follows: Based on the condensation precipitation rate, condensation flow rate, and condensation latent heat release rate of the refrigeration equipment at each time point, analyze the condensation release characteristic value at the corresponding time point. Specifically, the condensation precipitation rate, condensation flow rate, and condensation latent heat release rate of the refrigeration equipment at each time point are standardized, and the results of the standardization are weighted to obtain the condensation release characteristic value at the corresponding time point. This value is used to characterize the comprehensive ability of the refrigeration equipment to condense and discharge water vapor in the air at that moment. The larger the value, the stronger the condensation effect, the smoother the drainage, and the lower the outlet dew point temperature.

[0088] Based on the water accumulation height, condensate film thermal resistance, and condensation phase change equilibrium value of the refrigeration equipment at each time point, the condensation stagnation characteristic value at the corresponding time point is analyzed. Specifically, the water accumulation height, condensate film thermal resistance, and condensation phase change equilibrium value of the refrigeration equipment at each time point are standardized, and the standardized results are weighted to obtain the condensation stagnation characteristic value at the corresponding time point. This value is used to characterize the degree of stagnation in the refrigeration equipment during condensation heat exchange and drainage at that moment. The larger the value, the more serious the condensate retention, the obstructed heat exchange, or the drainage imbalance, and the higher the outlet dew point temperature.

[0089] In this implementation scheme, through in-depth analysis of the condensation state time series data, the parameters related to dew point in the condensation process are transformed into characteristic values ​​reflecting dew point control, thereby more accurately assessing the impact of condensation and drainage on the dryness of the outlet air. Secondly, the condensation precipitation rate and the latent heat release rate reflect the strength of water vapor condensation, while the condensation flow rate reflects the smoothness of the drainage process. The combination of these three values ​​reveals the overall efficiency of the condensation process. Meanwhile, the water accumulation height, condensate film thermal resistance, and condensation phase change equilibrium reveal the hindrance phenomenon. Finally, by analyzing the condensation release characteristic value and condensation hindrance characteristic value through these parameters, and by weighting and correcting them in the final characteristic value generation process, the promoting and inhibiting effects of the condensation process are taken into account. This ensures that the obtained condensation dew point control characteristic value can reflect the impact of the condensation process on the dew point, thereby improving the accuracy of control and ensuring a more reliable drying effect of compressed air.

[0090] Specifically, the steps for analyzing and setting the sound pressure dew point control characteristic value of the refrigeration equipment are as follows: Input the compressed sound pressure signal data of the refrigeration equipment into the pre-trained sound pressure dew point mapping model, and analyze the sound pressure mapping characteristic set of the refrigeration equipment, including sound pressure impact intensity characteristic value, harmonic leakage fluctuation characteristic value, and frequency band offset equalization characteristic value; Based on the sound pressure mapping characteristic set of the refrigeration equipment, analyze the sound pressure dew point control characteristic value of the refrigeration equipment (used to characterize the ability of the refrigerated air dryer to control the outlet air dew point temperature under the compressor sound pressure state; the larger the value, the better the operating state, the smoother the refrigerant circulation, the more sufficient the evaporator heat exchange, and the lower the outlet dew point temperature), the specific formula is as follows:

[0091] ;in, To set the sound pressure dew point control characteristic value for refrigeration equipment, To set the characteristic value of sound pressure impact intensity for refrigeration equipment, The sound pressure impact adjustment coefficients are stored in the database. To set the characteristic value of harmonic leakage fluctuation of refrigeration equipment, The leakage fluctuation adjustment coefficient is stored in the database. To set the frequency band offset equalization characteristic value for the refrigeration equipment, The frequency band offset adjustment coefficients are stored in the database. The smoothing adjustment coefficients are stored in the database, and in this embodiment, the sound pressure impact adjustment coefficients are stored in the database. Leakage fluctuation adjustment coefficient Frequency band offset adjustment coefficient Smoothing adjustment coefficient The values ​​were 0.385, 0.437, 0.482, and 3.000, respectively.

[0092] The compressed sound pressure signal data is specifically the compressed sound pressure amplitude at each time point. The sound pressure dew point mapping model includes an input partitioning layer, a sound pressure coding layer, a sound pressure time-varying layer, and an output layer.

[0093] The specific steps for analyzing and setting the sound pressure mapping feature set of the refrigeration equipment are as follows: In the input partitioning layer of the sound pressure dew point mapping model, the compressed sound pressure signal data of the refrigeration equipment is received and divided into several frames of sound pressure signals of the refrigeration equipment. Specifically, the compressed sound pressure signal is bandpass filtered to filter out mechanical vibration noise below 50Hz and random environmental noise above 8kHz, retaining only the effective acoustic components related to compressor operation in the 50Hz~8kHz frequency band. The compressed sound pressure signal after bandpass filtering is divided according to the preset frame length (e.g., 20ms~40ms), and the set overlap length (e.g., 50% frame length) is set between adjacent frames to obtain several frames of sound pressure signals, including the compressed sound pressure amplitude at several time points in the frame.

[0094] In the sound pressure coding layer of the sound pressure dew point mapping model, the sound pressure feature vector of the corresponding frame is extracted based on several frames of sound pressure signals from the set refrigeration equipment. In the sound pressure time-varying layer of the sound pressure dew point mapping model, the sound pressure mapping time-series feature vector of the set refrigeration equipment is extracted based on the sound pressure feature vector of each frame. Specifically, this layer adopts LSTM. LSTM processes the input sequence data step by step through a recurrent structure. At each time step, the LSTM unit uses the input gate, forget gate, and output gate mechanism to filter and update the sound pressure feature vector, thereby suppressing irrelevant noise information while retaining important information. During this process, the hidden state is continuously updated as the time step progresses, enabling the network to capture the dynamic change pattern of sound pressure features in the time series and maintain the memory of long-term dependencies. Through this process, the sound pressure mapping time-series feature vector reflecting the time-series evolution law of sound pressure during the operation of the refrigeration equipment can be extracted, such as:

[0095] The sound pressure impact features in the sound pressure feature vector of each frame are processed by moving average to extract the sound pressure impact intensity features, which are used to characterize the overall intensity level of the compressor's suction and discharge impact in consecutive frames. When it is high, it indicates that the compressor's suction and discharge actions are powerful and sufficient, the refrigerant flow is sufficient, the heat exchange capacity of the evaporator is enhanced, thereby reducing the outlet dew point temperature.

[0096] The harmonic energy leakage features in the sound pressure feature vector of each frame are subjected to variance processing to extract the harmonic leakage fluctuation features, which are used to characterize the degree of energy leakage fluctuation during compressor operation. When the value increases, it indicates that more energy is dispersed on non-integer multiple harmonics, and there are abnormalities such as friction, leakage or unstable load in the equipment operation, which reduces the refrigerant cycle efficiency and causes the outlet dew point temperature to rise.

[0097] The frequency band energy distribution offset features in the sound pressure feature vector of each frame are averaged to extract the frequency band offset equalization feature, which is used to characterize the average distribution of sound pressure energy among different working frequency bands in low, mid and high frequencies. When the value is large, it indicates that the airflow circulation is smooth, the evaporator can exchange heat efficiently, and the dew point temperature drops. The sound pressure impact intensity feature, harmonic leakage fluctuation feature, and frequency band offset equalization feature are then concatenated into a sound pressure mapping time sequence feature vector.

[0098] In the output layer of the sound pressure dew point mapping model, based on the set sound pressure mapping time sequence feature vector of the refrigeration equipment, the set sound pressure mapping feature set of the refrigeration equipment is output. Specifically, the sound pressure impact intensity feature, harmonic leakage fluctuation feature, and frequency band offset equalization feature in the sound pressure mapping time sequence feature vector are activated by the Sigmoid function to obtain the sound pressure impact intensity feature value, harmonic leakage fluctuation feature value, and frequency band offset equalization feature value between 0 and 1.

[0099] The specific steps for extracting the sound pressure feature vector of each frame of the set cooling device are as follows: For each frame of sound pressure signal, the compressed sound pressure amplitude at each time point is averaged to obtain the average compressed sound pressure of that frame. The average compressed sound pressure amplitude at each time point is then compared with the average compressed sound pressure. The sum of positive and negative differences (absolute values ​​are taken here) is calculated and ratios are performed to extract the sound pressure bias symmetry factor of that frame. Based on the compressed sound pressure amplitude at each time point of each frame of sound pressure signal, several local maxima (i.e., the compressed sound pressure amplitude at a certain time point is higher than the compressed sound pressure amplitude at the previous and next time points) are identified. The sound pressure amplitude is then calculated by taking the time point as the local maximum. The compressed sound pressure amplitude at each local maximum is squared and summed to obtain the local maximum energy value of the frame. Simultaneously, the compressed sound pressure amplitude at each time point of the frame is squared and summed to obtain the total energy value of the frame. The ratio is then calculated as local maximum energy value / total energy value to extract the impact energy factor. This factor is then weighted with the sound pressure offset symmetry feature to extract the sound pressure impact feature, which is used to characterize the overall effectiveness of the compressor's intake and exhaust impact within a single frame. When the impact factor is high, it indicates that the compressor's intake and exhaust impact is strong and stable, the evaporator has sufficient cooling capacity, and the outlet dew point temperature is reduced.

[0100] For each frame of sound pressure signal, a Fast Fourier Transform is performed on the compressed sound pressure amplitude at each time point to obtain the spectral amplitude distribution of the signal, i.e., several frequency components (corresponding to a discrete frequency point) and their corresponding amplitudes. The spectral energy value (i.e., the square of the amplitude) of each frequency component is counted, and the frequency component with the largest frequency energy value is identified as the dominant frequency component and defined as the fundamental frequency of the signal frame. Integer multiples of the fundamental frequency are used as harmonic reference points. At each integer multiple frequency, a preset frequency tolerance range (e.g., ±5% of the fundamental frequency) is set, and the spectral energy within this range is used as the standard. Quasi-harmonic energy is obtained by summing the remaining spectral energy outside the tolerance range after extracting energy at all integer multiple frequencies. Simultaneously, the total spectral energy of the entire frame is summed to obtain the total spectral energy value for that frame. Finally, the ratio of the non-integer multiple harmonic energy value to the total spectral energy value is calculated to extract the harmonic energy leakage characteristics of that frame. This characteristic characterizes the degree of abnormality in the compressor's suction and discharge processes during operation in that frame. A higher value indicates a decrease in refrigerant circulation efficiency and insufficient heat exchange in the evaporator during compressor operation, leading to an increase in the outlet dew point temperature.

[0101] The spectral energy value of each frequency component in each frame of the sound pressure signal is read. Based on the operating characteristics of the refrigerated air dryer compressor stored in the database, the frequency range is divided into low-frequency band (50–500Hz), mid-frequency band (500–2000Hz), and high-frequency band (2000–8000Hz). According to the interval where the frequency point corresponding to each frequency component is located, the corresponding spectral energy values ​​are accumulated to obtain the low-frequency energy value, mid-frequency energy value, high-frequency energy value, and total energy value. The low-frequency energy value, mid-frequency energy value, and high-frequency energy value are then compared with the total energy value. Ratio processing is performed to obtain low-frequency, mid-frequency, and high-frequency proportions. The mid-frequency and high-frequency proportions are then differenced (the absolute value of the result is taken), and the result is compared with the low-frequency proportion to extract the frequency band energy distribution shift feature of the frame. This feature is used to characterize the distribution of sound pressure energy in different operating frequency bands. When the shift is large, it indicates that the compressor's intake and exhaust and refrigerant circulation processes are stable, the evaporator heat exchange is sufficient, and the outlet dew point temperature is reduced. The sound pressure impact feature, harmonic energy leakage feature, and frequency band energy distribution shift feature are concatenated into a sound pressure feature vector.

[0102] Furthermore, the pre-training steps for the sound pressure dew point mapping model are as follows:

[0103] A sound pressure labeling dataset was obtained, which consists of compressed sound pressure signal data of several refrigerated air dryers under different operating conditions and the corresponding true values ​​of outlet air dew point temperature. The data was acquired by experimental personnel by deploying sound pressure sensors and dew point thermometers at the operating site, and labeled by refrigeration engineering experts based on the measured results. Each sample in the sound pressure labeling dataset includes a sequence of compressed sound pressure signal frames of the set refrigeration equipment in multiple consecutive time periods, as well as the corresponding outlet dew point temperature label for that time period. The dataset is divided into training set, validation set, and test set. For example, 80% of the data is used for training, 10% for validation, and 10% for testing.

[0104] The sound pressure dew point mapping model is trained. Taking the sound pressure time-varying layer as an example, the sound pressure feature vector of each frame is input into LSTM (Long Short-Term Memory) network for temporal feature extraction. The LSTM layer controls the information flow through input gate, forget gate and output gate mechanism, learns the long-term dependency relationship between each time step, and thus captures the dynamic change pattern of sound pressure features over time. The output layer of the model generates a sound pressure dew point mapping feature set (including sound pressure impact intensity feature value, harmonic leakage fluctuation feature value and frequency band offset equalization feature value), and compares it with the corresponding dew point temperature label to calculate the prediction error.

[0105] During training, optimization algorithms (such as the Adam optimizer) are used to minimize the loss function (e.g., mean squared error, MSE), and the network parameters are updated through backpropagation (BPTT). Hyperparameters (such as learning rate, number of LSTM hidden layer units, batch size, etc.) can be adjusted during training to improve the model's fitting ability and stability. The training effect is evaluated through a validation set to avoid overfitting. Finally, the generalization ability of the model is tested on a test set to ensure that it can accurately predict the sound pressure-dew point relationship under unseen working conditions.

[0106] After training, the optimal model parameters are saved for deployment in subsequent refrigeration equipment operation monitoring, enabling online input of real-time sound pressure signals and output of feature values.

[0107] In this implementation scheme, a pre-trained sound pressure dew point mapping model is used to extract and analyze the compression sound pressure signal frame by frame, thereby converting the complex compressor sound pressure signal into specific feature values. This provides a new basis for dew point control. For example, the sound pressure impact intensity feature can reflect the strength and stability of the compressor's intake and exhaust. If this value is high, it indicates that the refrigerant circulation is smooth and the evaporator heat exchange is more sufficient. The harmonic leakage fluctuation feature reveals the distribution of energy on non-integer multiple harmonics. Its large value often indicates abnormalities such as friction or leakage during operation, corresponding to the risk of increased dew point temperature. The frequency band offset balance feature reflects the rationality of the distribution of acoustic energy in different frequency bands. When it is large, it means that the airflow circulation is smooth and the heat exchange efficiency is high. Furthermore, by introducing LSTM, the above features can not only capture the instantaneous state, but also reflect the continuity and trend of the operation process. This makes the sound pressure dew point control feature value a dynamic relationship reflecting the relationship between the equipment operating status and the dew point temperature, thereby making the dew point control more comprehensive and the drying effect of the outlet air more stable and reliable.

[0108] Please see Figure 4 This invention provides a technical solution: a control system for a refrigeration device, comprising: a data acquisition module for acquiring air heat exchange time-series data, compression sound pressure signal data, and condensation state time-series data of a set refrigeration device; a heat exchange and condensation dew point control analysis module for analyzing the heat exchange dew point control characteristic value and the condensation dew point control characteristic value of the set refrigeration device based on the air heat exchange time-series data and the condensation state time-series data of the set refrigeration device, respectively; a sound pressure dew point control analysis module for analyzing the sound pressure dew point control characteristic value of the set refrigeration device based on a pre-trained sound pressure dew point mapping model and combined with the compression sound pressure signal data of the set refrigeration device; and a combined dew point control module for performing combined dew point control on the set refrigeration device based on the heat exchange dew point control characteristic value, the condensation dew point control characteristic value, and the sound pressure dew point control characteristic value.

[0109] Although preferred embodiments of the invention have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including both the preferred embodiments and all changes and modifications falling within the scope of the invention.

[0110] Obviously, those skilled in the art can make various modifications and variations to this invention without departing from its spirit and scope. Therefore, if these modifications and variations fall within the scope of the claims of this invention and their equivalents, this invention also intends to include these modifications and variations.

Claims

1. A control method for a refrigeration device, characterized in that, Includes the following steps: Acquire the air heat exchange time sequence data, compression sound pressure signal data, and condensation state time sequence data of the set refrigeration equipment. The air heat exchange time sequence data includes the drying load factor, flow rate disturbance value, evaporation surface temperature difference value, evaporation heat exchange driving force value, evaporation airflow resistance factor, and outlet air saturation deviation value at each time point. Based on the air heat exchange time series data and condensation state time series data of the set refrigeration equipment, the heat exchange dew point control characteristic value and condensation dew point control characteristic value of the set refrigeration equipment are analyzed respectively. The specific steps for analyzing and setting the characteristic values ​​for heat exchange dew point control of refrigeration equipment are as follows: Based on the air heat exchange time series data of the set refrigeration equipment, the performance dew point adjustment time series characteristic set of the set refrigeration equipment is analyzed, including the air drying performance characteristic value and evaporation heat exchange performance characteristic value at each time point; Based on the set of performance dew point adjustment time sequence characteristics of the refrigeration equipment, the heat exchange dew point driving characteristic values ​​at the corresponding time points are analyzed. Based on the heat exchange dew point driving characteristic value of the set refrigeration equipment at each time point, the heat exchange dew point regulation characteristic value of the set refrigeration equipment is analyzed. Based on a pre-trained sound pressure dew point mapping model and combined with the compressed sound pressure signal data of the refrigeration equipment, the sound pressure dew point regulation characteristic values ​​of the refrigeration equipment are analyzed, specifically as follows: The compressed sound pressure signal data of the set refrigeration equipment is input into the pre-trained sound pressure dew point mapping model to analyze the sound pressure mapping feature set of the set refrigeration equipment, including sound pressure impact intensity feature value, harmonic leakage fluctuation feature value, and frequency band offset equalization feature value. Based on the sound pressure mapping feature set of the refrigeration equipment, the sound pressure dew point control characteristic value of the refrigeration equipment is analyzed. The dew point of the set refrigeration equipment is controlled by combining the characteristic values ​​of heat exchange dew point regulation, condensation dew point regulation, and sound pressure dew point regulation.

2. The control method for the refrigeration equipment according to claim 1, characterized in that, The specific steps for analyzing and setting the performance dew point adjustment timing characteristic set of refrigeration equipment are as follows: Based on the drying load factor, flow rate disturbance value, and outlet air saturation deviation value of the refrigeration equipment at each time point, the air drying efficiency characteristic value at the corresponding time point is analyzed. Based on the evaporation surface temperature difference, evaporation heat transfer driving force, and evaporation airflow resistance factor of the refrigeration equipment at each time point, the characteristic values ​​of its evaporation heat transfer efficiency at the corresponding time points are analyzed.

3. The control method for the refrigeration equipment according to claim 1, characterized in that, The condensation state time-series data includes the condensation precipitation rate, water accumulation height, condensation flow rate, latent heat release rate, condensate film thermal resistance, and condensation phase change equilibrium value at each time point. The specific steps for analyzing and setting the condensation dew point control characteristic value of the refrigeration equipment are as follows: Based on the time-series data of the condensation state of the refrigeration equipment, the time-series characteristic set of the condensation dew point adjustment of the refrigeration equipment is analyzed, including the condensation release characteristic value and condensation resistance characteristic value at each time point. Based on the set of timing characteristics of condensation dew point adjustment of refrigeration equipment, the characteristic values ​​of condensation dew point control of refrigeration equipment are analyzed.

4. The control method for the refrigeration equipment according to claim 3, characterized in that, The specific steps for analyzing and setting the timing characteristic set of the condensation dew point adjustment for refrigeration equipment are as follows: Based on the condensation precipitation rate, condensation flow rate, and condensation latent heat release rate of the refrigeration equipment at each time point, analyze the condensation release characteristic values ​​at the corresponding time points. Based on the water accumulation height, condensate film thermal resistance, and condensation phase change equilibrium value of the refrigeration equipment at each time point, the condensation resistance characteristic value at the corresponding time point is analyzed.

5. The control method for the refrigeration equipment according to claim 1, characterized in that, The compressed sound pressure signal data is specifically the compressed sound pressure amplitude at each time point, and the sound pressure dew point mapping model includes an input partitioning layer, a sound pressure coding layer, a sound pressure time-varying layer, and an output layer.

6. The control method for the refrigeration equipment according to claim 5, characterized in that, The specific steps for analyzing and setting the sound pressure mapping feature set of the refrigeration equipment are as follows: In the input partitioning layer of the sound pressure dew point mapping model, the compressed sound pressure signal data of the set refrigeration equipment is received and divided into several frames of sound pressure signals of the set refrigeration equipment. In the sound pressure coding layer of the sound pressure dew point mapping model, the sound pressure feature vector of the corresponding frame is extracted based on several frames of sound pressure signals of the set refrigeration equipment. In the sound pressure time-varying layer of the sound pressure dew point mapping model, the sound pressure mapping time sequence feature vector of the set refrigeration equipment is extracted based on the sound pressure feature vector of each frame of the set refrigeration equipment. In the output layer of the sound pressure dew point mapping model, the sound pressure mapping feature set of the set refrigeration equipment is output based on the time-series feature vector of the sound pressure mapping of the set refrigeration equipment.

7. The control method for the refrigeration equipment according to claim 1, characterized in that, The specific steps for combined dew point control of a set refrigeration device based on heat exchange dew point control characteristic values, condensation dew point control characteristic values, and sound pressure dew point control characteristic values ​​are as follows: The characteristic values ​​of heat exchange dew point control, condensation dew point control, and sound pressure dew point control of the refrigeration equipment are normalized. The normalized dew point control characteristic values ​​of the set refrigeration equipment, including heat exchange dew point control characteristic values, condensation dew point control characteristic values, and sound pressure dew point control characteristic values, are compared with several preset dew point adjustment ranges for judgment and analysis. Based on the judgment and analysis results, corresponding dew point control measures are taken for the set refrigeration equipment.

8. A control system for a refrigeration device, employing the control method for the refrigeration device according to any one of claims 1-7, characterized in that, include: The data acquisition module is used to acquire air heat exchange timing data, compression sound pressure signal data, and condensation state timing data of the set refrigeration equipment; The heat exchange condensation dew point control analysis module is used to analyze the heat exchange dew point control characteristic value and condensation dew point control characteristic value of the set refrigeration equipment based on the air heat exchange time series data and condensation state time series data of the set refrigeration equipment, respectively. The sound pressure dew point control analysis module is used to analyze the sound pressure dew point control characteristic value of the set refrigeration equipment based on the pre-trained sound pressure dew point mapping model and combined with the compressed sound pressure signal data of the set refrigeration equipment. The combined dew point control module is used to perform combined dew point control on the set refrigeration equipment based on the heat exchange dew point regulation characteristic value, condensation dew point regulation characteristic value, and sound pressure dew point regulation characteristic value.

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