Light-mix energy-saving dehumidifier control method and system

Abstract

The present application relates to a kind of light mixed energy-saving dehumidifier control method and system, it is related to the field of energy-saving technology, it includes: by gathering condensing heat of air supply refrigeration system, regenerative air inlet temperature and outlet temperature data, extract heat recovery characteristics and determine system heat state, further match light mixed energy-saving or traditional heating mode;When heat recovery does not meet preheating demand, start high-grade heat source compensation heating.At the same time, collect dehumidification area humidity and image information, locate the highest humidity area, plan obstacle avoidance dehumidification path, combine with environmental wind parameter dynamic correction air supply and deflector parameter, realize accurate area dehumidification.The present application has the effect of improving the overall energy efficiency of dehumidification system.

Description

Technical Field

[0001] This invention relates to the field of energy-saving technology, and in particular to a control method and system for a mild hybrid energy-saving dehumidifier. Background Technology

[0002] A dehumidifier is an air handling device used to reduce the moisture content in the air and maintain a specific humidity environment in a space.

[0003] In the industrial sector, rotary dehumidification systems are the mainstream dehumidifier solution. Fresh air is filtered and pre-dehumidified by a surface cooler, then mixed with return air, filtered and cooled again before entering the dehumidification rotor for deep dehumidification. After being mixed with a second batch of return air, it is pressurized by a processing fan, filtered through a medium-efficiency filter, cooled by a supply air surface cooler, and then sent to the drying workshop. The filtered fresh air is then heated to 120-130°C by a regeneration heater, regenerated by the rotor, and discharged by a regeneration fan.

[0004] Its regenerative heating requires raising the fresh air temperature from room temperature to 120 to 130°C, while cooling requires continuously cooling the air on the treatment side. Both of these have extremely high energy consumption in spring, summer, and autumn, and the cold and heat energy are not effectively utilized in synergy, resulting in low overall energy efficiency of the dehumidification system, which needs to be improved. Summary of the Invention

[0005] To improve the overall energy efficiency of dehumidification systems, this invention provides a control method and system for a mild hybrid energy-saving dehumidifier.

[0006] In a first aspect, the present invention provides a control method for a mild hybrid energy-saving dehumidifier, which adopts the following technical solution: A control method for a mild hybrid energy-saving dehumidifier includes: Collect preset information on the condensation heat of the air supply cooling system and the inlet temperature of the regenerated air; Heat recovery characteristics are extracted based on condensation heat information, and combined with inlet temperature information to determine the system thermal state; The regenerative heating mode is determined based on the system's thermal state; Collect preset outlet temperature data of the regenerative preheater; Based on the condensation heat information and outlet temperature data, determine whether the heat recovery meets the preheating requirements; When heat recovery does not meet the preheating requirements, a preset compensation heater is activated to heat the regenerated air based on the regeneration heating mode.

[0007] By adopting the above technical solution, the system first collects information on the condensation heat of the supply air cooling system and the inlet temperature of the regenerated air. Based on the condensation heat, heat recovery characteristics are extracted, and the system's thermal state is determined in conjunction with the inlet temperature, thus determining the regeneration heating mode. Next, the outlet temperature data of the regeneration preheater is collected, and combined with the condensation heat information, it is determined whether the heat recovery meets the preheating requirements. If not, the compensation heater is activated to heat the regenerated air according to the regeneration heating mode. In this way, the condensation heat generated by the supply air cooling system is recovered for preheating the regenerated air, achieving the synergistic utilization of cold and heat energy within the system. Simultaneously, the regeneration heating mode is dynamically adjusted according to the system's thermal state, and the outlet temperature data accurately determines whether heat recovery meets the standards, activating the compensation heater only when necessary, reducing additional energy consumption. This mechanism effectively reduces the overall energy consumption of the regeneration heating and cooling process, solves the problem of low cold and heat energy utilization in traditional systems, and thus improves the overall energy efficiency of the dehumidification system.

[0008] Optionally, the regenerative heating mode includes a mild hybrid energy-saving mode and a conventional heating mode, wherein the mild hybrid energy-saving mode includes: Collect supply air temperature and humidity parameters; The characteristics of the supply air cooling load are obtained based on the supply air temperature and humidity parameters. The heat recovery power is determined by combining the characteristics of the supply air cooling load and the information on condensation heat. Configure preheating parameters based on heat recovery power and inlet temperature information; The preheating operation of the preheating preheater is controlled based on the preheating parameters.

[0009] By adopting the above technical solution, in the mild hybrid energy-saving mode, the temperature and humidity parameters of the supply air are first collected to obtain the supply air cooling load characteristics. These characteristics, combined with condensation heat information, determine the heat recovery power. Then, based on the heat recovery power and the regenerated air inlet temperature, preheating parameters are configured. Finally, the regenerated preheater is controlled to perform preheating operations based on these preheating parameters. This heating mode, which primarily recovers waste heat, minimizes the additional energy consumption of regenerated heating, fully leverages the advantages of mild hybrid energy saving, and further improves the energy efficiency ratio of the dehumidification system.

[0010] Optionally, the conventional heating mode includes: Collect available state parameters of high-grade heat sources and target air temperature of regenerated air; The temperature difference is obtained by matching the preset regeneration temperature value with the system thermal state. The compensation heating amount is matched based on the temperature difference; Based on available state parameters and compensation heating amount, generate compensation heating command; In response to a compensation heating command, a preset compensation heater is controlled to heat the preheated regenerated air until the target air temperature is reached.

[0011] By adopting the above technical solution, in the traditional heating mode, the available state parameters of the high-grade heat source and the target temperature of the regenerated air are first collected. The regenerated temperature value is matched from the system thermal state to calculate the temperature difference. Based on the temperature difference, the required compensation heating amount is determined. Then, combined with the available state parameters of the high-grade heat source, a compensation heating command is generated. Finally, in response to the command, the compensation heater is controlled to heat the preheated regenerated air to the target temperature. This mode, as a supplement to the mild hybrid energy-saving mode, can maintain system performance under extreme operating conditions while reducing unnecessary energy consumption through quantitative control, achieving a balance between energy efficiency and reliability.

[0012] Optional, also includes: Collect the temperature of the supplied air; The supply air temperature difference is determined based on the supply air temperature and the preset target supply air temperature. Determine whether the supply air temperature difference exceeds the preset temperature difference threshold; When the supply air temperature difference exceeds the temperature difference threshold, the preset precooler is activated to absorb the heat of the supply air. When the supply air temperature difference does not exceed the temperature difference threshold, the preset precooler is kept off.

[0013] By adopting the above technical solution, the temperature of the supplied air is first collected, and the difference between it and the preset target supplied air temperature is calculated. It is then determined whether this difference exceeds a temperature difference threshold. If it does, the precooler is activated to absorb heat from the supplied air; otherwise, the precooler remains closed. This reduces the additional energy consumption in the refrigeration process and, in conjunction with the regenerative heating heat recovery mechanism, optimizes the overall energy efficiency of the dehumidification system.

[0014] Optional, also includes: Collect humidity information for the preset dehumidification area; Determine humidity distribution characteristics based on regional humidity information; Determine the area with the highest humidity based on humidity distribution characteristics; The dehumidifier is controlled to perform dehumidification of the area with the highest humidity using a preset cycle dehumidification method.

[0015] By adopting the above technical solution, the humidity information of the dehumidification area is first collected, the humidity distribution characteristics are analyzed and the area with the highest humidity is determined, and then the dehumidifier is controlled to dehumidify the area in a targeted manner using a turnover dehumidification method. This improves the dehumidification efficiency, shortens the time for the system to reach the target humidity, and further optimizes the energy efficiency performance of the dehumidification system.

[0016] Optionally, the turnover dehumidification method includes: Determine the initial dehumidification range based on the area with the highest humidity; The turnover dehumidification path is obtained based on the initial dehumidification range; Control the dehumidifier to circulate air according to the circulation dehumidification path, and collect real-time humidity distribution data during the circulation air circulation process; Combine real-time humidity distribution data and turnover dehumidification path to generate dynamic dehumidification range; The system updates the turnover dehumidification path based on the dynamic dehumidification range and controls the dehumidifier to perform precise zone dehumidification based on the updated turnover dehumidification path.

[0017] By adopting the above technical solution, an initial dehumidification range is first determined based on the area with the highest humidity, and a revolving dehumidification path is planned. The dehumidifier is then controlled to circulate and deliver air along this path. During the air delivery process, real-time humidity distribution data is collected, and combined with this data and the original path to generate a dynamic dehumidification range. This process then updates the revolving path, achieving precise regional dehumidification. This approach overcomes the limitations of fixed-range dehumidification by dynamically adjusting the dehumidification range and path based on real-time humidity data. Simultaneously, this dynamic adjustment ensures that dehumidification resources are always focused on the areas most in need of dehumidification, reducing unnecessary energy consumption in low-humidity areas. This adaptive revolving strategy significantly improves energy utilization efficiency while maintaining dehumidification effectiveness.

[0018] Optional, also includes: Collect regional image information of the dehumidification area; Obstacle distribution information is obtained by identifying regional image information; Obstacle contour features are determined based on obstacle distribution information; The obstacle avoidance and dehumidification path is generated by combining obstacle outline features and real-time humidity distribution data. Optimal air supply parameters are calculated based on the obstacle avoidance and dehumidification path. The dehumidifier is controlled to dehumidify according to the obstacle avoidance dehumidification path, while the air supply direction and air supply intensity are adjusted based on the optimal air supply parameters.

[0019] By adopting the above technical solution, image information of the dehumidification area is first collected to identify the distribution and contour features of obstacles. This information is then combined with real-time humidity distribution data to generate an obstacle-avoidance dehumidification path. Next, optimal air supply parameters are calculated based on the path, controlling the dehumidifier to dehumidify along the obstacle-avoidance path, and adjusting the air supply direction and intensity according to the parameters. This approach solves the problem of obstacles obstructing the dehumidification airflow. By identifying obstacle contours and planning obstacle-avoidance paths, it avoids localized dehumidification ineffectiveness caused by blocked dehumidification airflow. Simultaneously, the optimal air supply parameters ensure that the dehumidification airflow efficiently reaches high-humidity areas, reducing energy waste caused by airflow obstruction.

[0020] Optional, also includes: Collect current environmental wind parameters; The environmental wind influencing factor is calculated based on environmental wind parameters and obstacle avoidance and dehumidification paths. The optimal air supply parameters are adjusted based on environmental wind influencing factors. Adjust the air supply direction and intensity based on the corrected optimal air supply parameters.

[0021] Optional, also includes: The control parameters for the air guide plate are generated based on the obstacle avoidance and dehumidification path and the outline features of the obstacles. The air guide plate, which is pre-set on the dehumidifier, is deployed based on the control parameters of the air guide plate. Collect ambient wind force, ambient wind direction, and ambient wind turbulence intensity; The control parameters of the wind deflector are corrected by combining the ambient wind force, ambient wind direction, ambient wind turbulence intensity, and wind deflector control parameters. Adjust the deployment angle and deflection direction of the air guide plate based on the revised control parameters.

[0022] By adopting the above technical solution, the control parameters for the air guide plate are first generated based on the obstacle avoidance and dehumidification path and the outline characteristics of the obstacle, and the deployment of the air guide plate is controlled. Then, the wind force, wind direction, and turbulence intensity of the ambient wind are collected, and these environmental factors are combined with the initial air guide plate control parameters for correction. Finally, the deployment angle and deflection direction of the air guide plate are adjusted based on the corrected parameters. This dual control ensures that the dehumidified airflow is always delivered to the target area efficiently, reducing ineffective energy consumption caused by airflow turbulence or obstruction, and further improving the energy efficiency and dehumidification accuracy of the dehumidification system.

[0023] Secondly, this application provides a mild hybrid energy-saving dehumidifier control system, which adopts the following technical solution: A mild hybrid energy-saving dehumidifier control system includes: The data acquisition module is used to collect information on condensation heat, inlet temperature, and outlet temperature. A memory for storing a program that implements a mild hybrid energy-saving dehumidifier control method; The processor is used to load and execute programs stored in memory.

[0024] In summary, this application includes at least one of the following beneficial technical effects: 1. By recovering the condensation heat generated by the air supply cooling system and using it to preheat the regenerated air, the system achieves synergistic utilization of cold and heat energy. Simultaneously, the regeneration heating mode is dynamically adjusted based on the system's thermal state, and the heat recovery is precisely assessed using outlet temperature data. The compensation heater is activated only when necessary, reducing additional energy consumption. This mechanism effectively reduces the overall energy consumption of the regeneration heating and cooling processes, solving the problem of low cold and heat energy utilization in traditional systems, thereby improving the overall energy efficiency of the dehumidification system. 2. In mild hybrid energy-saving mode, the temperature and humidity parameters of the supply air are first collected to obtain the supply air cooling load characteristics. These characteristics, combined with condensation heat information, determine the heat recovery power. Then, based on the heat recovery power and the regenerated air inlet temperature, preheating parameters are configured. Finally, the regenerated preheater is controlled to perform preheating operations based on these preheating parameters. This heating mode, which primarily recovers waste heat, minimizes the additional energy consumption of regenerated heating, fully leverages the advantages of mild hybrid energy saving, and further improves the energy efficiency ratio of the dehumidification system. 3. The dehumidification range and path are dynamically adjusted based on real-time humidity data. At the same time, the dynamic adjustment ensures that dehumidification resources are always focused on the areas that need the most dehumidification, reducing unnecessary energy consumption in low-humidity areas. This significantly improves energy utilization efficiency while ensuring dehumidification effect. Attached Figure Description

[0025] Figure 1 This is a flowchart of a control method for a mild hybrid energy-saving dehumidifier; Figure 2 This is a simplified diagram illustrating the operation of a dehumidifier during its turnover dehumidification process; Figure 3 This is a process flow diagram of a rotary dehumidifier; Figure 4 This is a process flow diagram of a mild hybrid energy-saving dehumidifier.

[0026] The parts referred to by the numbers in the above attached diagrams are as follows: 3. Dehumidifier; 4. Dehumidification path; 5. Dehumidification area; 6. Highest humidity area. Detailed Implementation

[0027] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments.

[0028] Reference Figure 1 , 2 3 and 4, embodiments of this application disclose a control method for a mild hybrid energy-saving dehumidifier. This method is applied to a mild hybrid energy-saving dehumidifier, wherein the regenerative heating of the mild hybrid energy-saving dehumidifier is divided into two parts. One part of the heating energy is provided by traditional high-quality heat sources such as electricity, steam, and thermal oil. The other part is regenerated by transferring the heat energy generated by the air supply cooling. In spring and autumn, the heat energy generated by the air supply cooling is mainly used as the regenerative heating energy. In summer, the heating from spring and autumn is supplemented by traditional high-quality heat sources such as electricity, steam, and thermal oil to reach 120 to 130°C. In the mild hybrid energy-saving dehumidifier, the air supply cooling is divided into two to three parts for cooling, as specifically implemented as follows: In this embodiment, the first part of the air supply cooling is achieved through the coordinated heat transfer and cooling of precooler 2# and regeneration preheater 1#. Specifically, precooler 2# is connected to the air supply path and absorbs heat from the air supply through heat exchange, effectively reducing the air supply temperature and thus reducing the load on subsequent cooling stages. Simultaneously, precooler 2# forms a closed-loop fluid circulation system with the compressor pump and regeneration preheater 1# via connecting pipes. The compressor pump, as a power source, drives the flow of heat transfer fluid (such as refrigerant like Freon) inside the connecting pipes, transferring the heat absorbed by precooler 2# to regeneration preheater 1#. Regeneration preheater 1# is connected to the regeneration fresh air path and releases heat as the heat transfer fluid flows through it, raising the temperature of the regeneration fresh air to 50-55°C after absorbing heat, laying the foundation for subsequent regeneration heating.

[0029] In addition, a storage tank and a separator are connected in series on the connecting pipe: the storage tank stores excess energy in the connecting pipe and can release or store energy when environmental conditions (such as fluctuations in supply air temperature and changes in regenerated fresh air volume) change, ensuring the stability of system operation; the separator separates the gaseous and liquid mixtures in the fluid in the connecting pipe, retaining only the liquid fluid to continue participating in the circulation, avoiding the gaseous fluid from affecting heat transfer efficiency. A mechanical shut-off valve is also installed on the side of the connecting pipe near the precooler 2#. This mechanical shut-off valve is used to cut off and reduce the pressure of the high-pressure liquid in the connecting pipe. Its opening degree is automatically controlled by a temperature sensor. The temperature sensor detects the temperature of the liquid in the connecting pipe after absorbing heat and transfers the corresponding heat to the inside of the shut-off valve. The expansion or contraction of the internal medium (such as the liquid in the temperature sensing bulb) pushes the valve needle to open or close, thereby adjusting the opening degree. In this embodiment, the mechanical shut-off valve is designed according to a standard superheat of 5K. When the superheat is less than 5K, it indicates that the fluid vaporization is insufficient, and the opening of the shut-off valve needs to be reduced to reduce the fluid flow rate and avoid wasting cooling capacity. When the superheat is greater than 5K, it indicates that the fluid vaporization is excessive, and the opening of the shut-off valve needs to be increased to increase the fluid flow rate and ensure refrigeration efficiency.

[0030] The second part of the air supply cooling system achieves deep heat recovery and cooling through the synergy of precooler 1# and regenerative preheater 2#. Precooler 1#, located downstream of precooler 2# in the air supply path, further absorbs residual heat from the supply air, continuously reducing the supply air temperature to meet the drying workshop's requirements for supply air temperature (typically below 16℃). Precooler 1# also forms a closed-loop circulation with another set of compressor pumps and regenerative preheater 2# via connecting pipes. The compressor pump drives the heat transfer fluid to transfer the heat absorbed by precooler 1# to regenerative preheater 2#. Regenerative preheater 2#, located downstream of regenerative fresh air in the fresh air path, has already been heated to 50-55℃ by regenerative preheater 1#. The heat released by regenerative preheater 2# is further absorbed by the fresh air, raising its temperature again to 80-85℃, significantly reducing the compensation heating load of subsequent high-grade heat sources. The connecting pipes of this circulation loop are also equipped with a storage tank and a separator, whose functions are the same as those of the storage tank and separator corresponding to the precooler #2 mentioned above, used for energy buffering and gas-liquid separation, respectively. Furthermore, this loop uses an electronic shut-off valve instead of a mechanical shut-off valve. The opening of the electronic shut-off valve is automatically adjusted by a dedicated controller: the controller presets a superheat threshold of 4 to 6K (preferably 5K in this embodiment), detects the actual temperature of the liquid after vaporization in the connecting pipe after heat absorption using a temperature sensor, and detects the saturation pressure of the liquid after vaporization in this state using a pressure sensor, feeding back the two real-time signals of temperature and pressure to the controller; the controller calculates the adjustment command based on the difference between the preset superheat and the actual superheat, generating a pulse signal to control the opening of the electronic shut-off valve—when the superheat is less than 5K, the opening is reduced to decrease the fluid flow rate; when the superheat is greater than 5K, the opening is increased to increase the fluid flow rate, achieving more precise control of cooling capacity and heat transfer.

[0031] exist Figure 4 In the system shown in the (process flow diagram of the light-mix energy-saving dehumidifier), the fresh air cooling and return air cooling of the light-mix energy-saving dehumidifier can use chilled water as the cooling source or Freon direct cooling as the cooling source. The specific cooling source type can be selected according to the user's site conditions and cost requirements. Whether or not to set up return air cooling and return air filtration can be determined according to the user's process requirements for air drying (such as the cleanliness and humidity accuracy of the drying workshop). For the supply air cooling stage, it is necessary to determine whether to add supply air cooling based on the actual cooling load of the supply air cooling: if the supply air temperature can be stably reduced to below 16℃ by the synergistic cooling of the precooler 1# and precooler 2#, then there is no need to set up additional supply air cooling; if the supply air temperature requirements still cannot be met, a supply air cooling needs to be added downstream of precooler 1# to supplement the cooling capacity and ensure that the supply air parameters meet the usage requirements of the drying workshop.

[0032] A control method for a mild hybrid energy-saving dehumidifier includes the following steps: S10: Collect the preset condensation heat information of the air supply cooling system and the inlet temperature information of the regenerated air.

[0033] A supply air cooling system refers to a system that cools and lowers the temperature of the supplied air. Supply air cooling systems are constructed in advance by those skilled in the art and will not be described in detail here.

[0034] Condensation heat information refers to the amount of heat released during the operation of the air-cooled system.

[0035] The condensation heat information is collected in real time by a heat metering device that is pre-installed in the condensation section of the refrigeration circuit in the air supply refrigeration system by a person skilled in the art.

[0036] Inlet temperature information refers to the temperature value of the regenerated air before it enters the regenerator preheater.

[0037] Inlet temperature information is obtained through a temperature sensor.

[0038] S11: Extract heat recovery characteristics based on condensation heat information and combine them with inlet temperature information to determine the system thermal state.

[0039] Heat recovery characteristics refer to the effective heat characteristic parameters of condensation heat that can be used for regeneration and preheating.

[0040] By understanding the condensation heat information, the heat output value per unit time is calculated. Combined with a pre-set heat recovery efficiency reference table, the proportion of actually usable heat is determined, forming the heat recovery characteristic parameters. The heat recovery efficiency reference table records the heat recovery efficiency values ​​under different operating conditions. This table was pre-established by those skilled in the art through system thermodynamic testing experiments and will not be elaborated upon here.

[0041] System thermal state refers to the state parameters that reflect the current supply and demand relationship of thermal energy in the system.

[0042] The system thermal state is determined by comparing the heat recovery characteristic parameters with the preset heat demand threshold, and combining the difference between the inlet temperature information and the preset target regeneration temperature, using a state assessment algorithm to calculate the system thermal state level.

[0043] The heat demand threshold refers to the minimum heat value required for system regeneration, which is preset by those skilled in the art based on the regeneration characteristics of the dehumidifying impeller.

[0044] The target regeneration temperature refers to the temperature required for the dehumidifier rotor to complete effective regeneration, which is preset by those skilled in the art based on the dehumidifier rotor model and process requirements.

[0045] The state assessment algorithm was designed by those skilled in the art based on the principle of system thermal balance, and will not be elaborated here.

[0046] S12: Determine the regenerative heating mode based on the system thermal state.

[0047] Regenerative heating mode refers to the method of heating regenerated air, including mild hybrid energy-saving mode and traditional heating mode.

[0048] Mild hybrid energy-saving mode refers to a hybrid heating method that prioritizes the use of condensation heat for preheating, supplemented by external heat source compensation heating. Specific details of the mild hybrid energy-saving mode will be explained in S20 to S24, and will not be elaborated upon here.

[0049] Traditional heating mode refers to a heating method that relies entirely on an external high-grade heat source. Specific details of traditional heating mode will be explained in S30 to S34 later, and will not be elaborated upon here.

[0050] The regenerative heating mode is determined by consulting a preset state mode lookup table. This table records the regenerative heating modes corresponding to different system thermal state levels. The state mode lookup table is preset by those skilled in the art based on the system's thermodynamic characteristics and energy efficiency optimization goals, and will not be elaborated here.

[0051] S13: Collect preset outlet temperature data of the regenerator preheater.

[0052] A regenerative preheater is a heat exchange device that uses recovered heat to preheat regenerated air.

[0053] The outlet temperature data refers to the temperature of the regenerated air after it has been heated by the preheater.

[0054] The outlet temperature data is collected in real time by a temperature sensor installed on the outlet pipe of the regenerator preheater.

[0055] S14: Determine whether heat recovery meets preheating requirements based on condensation heat information and outlet temperature data.

[0056] Preheating requirements refer to the minimum temperature that the regenerated air must reach before entering the main heater. These preheating requirements are predetermined by those skilled in the art based on the requirements of the dehumidification rotor regeneration process, and will not be elaborated upon here.

[0057] The outlet temperature data is compared with the preset target preheating temperature. Simultaneously, the difference between the condensation heat information and the required preheating heat is analyzed. A preheating evaluation algorithm is used to determine whether the heat recovery meets the preheating requirements. The target preheating temperature refers to the temperature threshold that the regenerated air needs to reach after preheating, which is preset by those skilled in the art based on system design parameters. The preheating evaluation algorithm is designed by those skilled in the art based on the principle of heat balance and will not be elaborated upon here.

[0058] S15: When heat recovery does not meet the preheating requirements, the pre-set compensation heater is activated to heat the regenerated air based on the regeneration heating mode.

[0059] A compensating heater is a device that uses a high-grade heat source to supplement the heating of regenerated air.

[0060] When heat recovery fails to meet preheating requirements, it means that the recovered condensation heat alone is insufficient to bring the regenerated air to the target preheating temperature. In this case, it is necessary to start the compensation heater to supplement the insufficient heat in order to heat the regenerated air.

[0061] The heating modes include mild hybrid energy-saving mode and traditional heating mode. The mild hybrid energy-saving mode includes: S20: Collect supply air temperature and humidity parameters.

[0062] Supply air temperature parameter refers to the temperature value of the supply air in its current state.

[0063] The supply air temperature parameter is obtained by a temperature sensor installed on the supply air duct.

[0064] Supply air humidity parameter refers to the percentage of humidity of the supply air under current conditions.

[0065] The humidity parameters of the supplied air are collected by a humidity sensor installed on the air supply duct.

[0066] S21: The characteristics of the supply air cooling load are obtained based on the supply air temperature parameters and supply air humidity parameters.

[0067] The characteristics of the supply air cooling load refer to the characteristic parameters that reflect the amount of heat that the supply air needs to remove.

[0068] First, based on the supply air temperature and humidity parameters, the current enthalpy value of the supply air is calculated using an enthalpy difference calculation model. This current enthalpy value is then compared with a preset target supply air state enthalpy value to obtain the enthalpy difference value that needs to be removed. Based on the enthalpy difference value and the supply air flow rate parameter, the characteristic value of the supply air cooling load is obtained using a cooling load calculation formula, thus yielding the supply air cooling load characteristics. The target supply air state enthalpy value is preset by those skilled in the art according to process requirements. The enthalpy difference calculation model and cooling load calculation formula are common knowledge in the fields of thermodynamics and HVAC, and will not be elaborated upon here.

[0069] S22: Combine the characteristics of the supply air cooling load and the information on condensation heat to determine the heat recovery power.

[0070] Heat recovery power refers to the amount of heat that can be used for regeneration preheating per unit time.

[0071] The theoretical condensation heat is compared with the actual collected condensation heat information, and the effective condensation heat is obtained by correcting it through the system energy efficiency model. Based on the effective condensation heat and the preset heat recovery efficiency coefficient, the actual usable heat recovery power value is obtained through the heat recovery power calculation model. The heat recovery efficiency coefficient is preset by those skilled in the art according to the characteristics of the heat exchanger; the system energy efficiency model and the heat recovery power calculation model are common knowledge in the field of thermodynamic system modeling, and will not be elaborated here.

[0072] S23: Configure preheating parameters based on heat recovery power and inlet temperature information.

[0073] Preheating parameters refer to the key parameters that control the operation of the regenerative preheater, including heat medium flow rate, heat exchange area, and preheating time.

[0074] The preheating parameters are determined by consulting a pre-set preheating parameter configuration table, which records the optimized preheating parameter values ​​corresponding to different combinations of heat recovery power and inlet temperature. The preheating parameter configuration table is pre-established by those skilled in the art through system thermal testing experiments. The specific table-building process is a conventional technical method in the field of thermal control and will not be elaborated here.

[0075] S24: Control the preset regenerative preheater to perform preheating operation based on preheating parameters.

[0076] A regenerative preheater is a heat exchange device that uses recovered heat to preheat regenerated air.

[0077] Preheating operation refers to adjusting the operating status of the regenerator according to the preheating parameters to achieve the preheating process of regenerated air.

[0078] Once the preheating parameters are obtained, the regenerative preheater needs to be controlled to preheat according to these parameters, so that the regenerated air can reach the preset first target temperature. The first target temperature refers to the initial temperature value that the regenerated air needs to reach after preheating, which is preset by those skilled in the art according to the system design, for example, 50°C. This facilitates the subsequent heat recovery unit to deeply heat the regenerated air with the generated heat during air supply cooling.

[0079] The subsequent heat recovery unit refers to a device that uses the high-temperature refrigerant generated by the refrigeration system to further heat the regenerated air.

[0080] Traditional heating modes include: S30: Collect available state parameters of the high-grade heat source and the target air temperature of the regenerated air.

[0081] Available status parameters refer to status information that reflects whether high-grade heat sources such as electric heating, steam heating, or thermal oil heating are currently available, including power supply status, steam valve opening degree, or thermal oil flow rate.

[0082] Available state parameters are acquired through the state monitoring sensors of the corresponding heat source.

[0083] The target air temperature refers to the final air temperature that the dehumidifier rotor needs to reach to complete regeneration and desorption.

[0084] The target air temperature is a fixed value in the range of 120 to 130°C, which is preset by those skilled in the art according to the requirements of the dehumidification rotor regeneration process, and will not be elaborated here.

[0085] S31: Match the preset regeneration temperature value from the system thermal state to obtain the temperature difference value.

[0086] The regeneration temperature value refers to the expected regeneration temperature of the system under different thermal states.

[0087] The regeneration temperature value is obtained by consulting a preset state temperature lookup table, which records the expected regeneration temperature values ​​corresponding to different system thermal state levels. The state temperature lookup table is pre-established by those skilled in the art based on the system's thermodynamic characteristics and operating data, and will not be elaborated upon here.

[0088] Temperature difference refers to the numerical difference between the target air temperature and the regeneration temperature.

[0089] The temperature difference is calculated by subtracting the regeneration temperature from the target air temperature.

[0090] S32: Match the compensation heating amount based on the temperature difference.

[0091] Compensation heating amount refers to the supplementary heat value that needs to be provided by the compensation heater.

[0092] The compensation heating amount is obtained by consulting a preset temperature difference heat reference table. This table records the compensation heating amount corresponding to different temperature differences. The temperature difference heat reference table is pre-established by those skilled in the art based on the system's heat capacity and heat transfer characteristics, and will not be elaborated here.

[0093] S33: Generate a compensation heating command based on available state parameters and compensation heating amount.

[0094] The compensating heating command is a drive signal that controls the compensating heater to perform heating operations.

[0095] The compensation heating command is generated through compensation control logic. This logic verifies the availability of the high-grade heat source based on available state parameters and, in conjunction with the compensation heating amount, queries a preset heating power mapping table to generate a control command containing specific power values ​​or valve opening parameters. The specific implementation of the compensation control logic is designed by those skilled in the art based on the heater type and control accuracy requirements, and will not be elaborated here. The heating power mapping table records the correspondence between the compensation heating amount and specific control parameters. The heating power mapping table is pre-established by those skilled in the art through thermodynamic calculations and experimental tests, and will not be elaborated here.

[0096] S34: In response to a compensation heating command, control a preset compensation heater to heat the preheated regenerated air until the target air temperature is reached.

[0097] A compensating heater is a device that uses a high-grade heat source to heat regenerated air.

[0098] Upon receiving a compensation heating command, the compensation heater must be controlled to perform the heating operation as required by the command. Simultaneously, the temperature of the regenerated air during the heating process must be monitored in real time. When the regenerated air temperature reaches the target air temperature, the heating operation should be automatically stopped. The specific temperature monitoring and control methods will be determined by those skilled in the art based on the system's accuracy requirements and will not be elaborated upon here.

[0099] Also includes: S40: Collects the temperature of the supplied air.

[0100] Supply air temperature refers to the real-time temperature value of the air in the supply air duct.

[0101] The temperature of the supplied air is obtained by a temperature sensor installed on the air supply duct.

[0102] S41: Determine the supply air temperature difference based on the supply air temperature and the preset target supply air temperature.

[0103] The target supply air temperature refers to the ideal temperature value that the supply air needs to reach.

[0104] The target supply air temperature is preset by those skilled in the art according to process requirements, and will not be elaborated here.

[0105] Supply air temperature difference refers to the numerical difference between the supply air temperature and the target supply air temperature.

[0106] The supply air temperature difference is calculated by subtracting the target supply air temperature from the supply air temperature.

[0107] S42: Determine whether the supply air temperature difference exceeds the preset temperature difference threshold.

[0108] The temperature difference threshold refers to the critical temperature difference value used to determine whether the precooler needs to be activated.

[0109] The temperature difference threshold is preset by those skilled in the art based on the system's cooling characteristics, and will not be elaborated here.

[0110] By determining whether the supply air temperature difference exceeds the temperature difference threshold, it can be determined whether the precooler needs to be activated.

[0111] S43: When the supply air temperature difference exceeds the temperature difference threshold, the preset precooler is activated to absorb the heat of the supply air.

[0112] A precooler is a heat exchange device that uses the principle of refrigerant evaporation to absorb heat and cool the supplied air.

[0113] When the temperature difference between the supply air and the temperature exceeds the temperature difference threshold, the precooler needs to be activated to absorb the excess heat in the supply air.

[0114] S44: When the supply air temperature difference does not exceed the temperature difference threshold, the preset precooler is kept off.

[0115] When the supply air temperature difference does not exceed the temperature difference threshold, there is no need to start the precooler; simply keep the precooler off.

[0116] Also includes: S50: Collect humidity information of the preset dehumidification zone 5.

[0117] Dehumidification zone 5 refers to a specific space that needs to maintain a dry environment, such as a drying workshop or warehouse. Dehumidification zone 5 is pre-defined by those skilled in the art and will not be elaborated upon here.

[0118] The area humidity information refers to the real-time humidity data set from multiple monitoring points within dehumidification zone 5. This area humidity information is collected by multiple humidity sensors distributed throughout dehumidification zone 5.

[0119] S51: Determine humidity distribution characteristics based on regional humidity information.

[0120] Humidity distribution characteristics refer to characteristic parameters that reflect the spatial distribution of humidity within the dehumidification zone 5.

[0121] The humidity dispersion characteristics are obtained by calculating the standard deviation of humidity data at each monitoring point; the humidity gradient characteristics, i.e., humidity distribution characteristics, are obtained by analyzing the humidity change rate between adjacent monitoring points using a gradient calculation model. The spatial statistical algorithm and gradient calculation model are common knowledge in the field of environmental monitoring and will not be elaborated upon here.

[0122] S52: Determine the area with the highest humidity based on the humidity distribution characteristics.

[0123] The highest humidity zone 6 refers to the local space range within dehumidification zone 5 where the humidity value remains the highest.

[0124] The highest humidity region 6 was identified by utilizing the humidity gradient feature in the humidity distribution characteristics to pinpoint the boundary area with the largest humidity change rate. Combined with humidity dispersion features, the core area where the humidity value consistently exceeds that of surrounding monitoring points was located. A spatial clustering algorithm was then used to cluster the high humidity monitoring points, determining the spatial range of the highest humidity region 6. The spatial clustering algorithm is common knowledge in the field of environmental monitoring and will not be elaborated upon here.

[0125] S53: Control the dehumidifier 3 to perform cycle dehumidification on the area 6 with the highest humidity using a preset cycle dehumidification method.

[0126] The turnover dehumidification method refers to a method of achieving rapid dehumidification by rotating the device around the area with the highest humidity 6. Specific details of the turnover dehumidification method will be explained in S60 to S64 later, and will not be repeated here.

[0127] The dehumidifier 3 is controlled to perform cyclic dehumidification on the highest humidity area 6 according to the cyclic dehumidification method, so as to ensure that the highest humidity area 6 obtains the maximum dehumidification effect.

[0128] Dehumidification methods include: S60: Determine the initial dehumidification range based on the highest humidity zone 6.

[0129] The initial dehumidification range refers to the initial dehumidification space range centered on the highest humidity zone 6, including the surrounding affected area.

[0130] The initial dehumidification range is determined by a spatial expansion algorithm. This algorithm is based on the spatial coordinates of the highest humidity region 6 and expands outward according to a preset expansion radius to form a circular or rectangular dehumidification region 5. The specific parameters of the spatial expansion algorithm are set by those skilled in the art based on the site characteristics and will not be elaborated here.

[0131] S61: Based on the initial dehumidification range, obtain the turnover dehumidification path 4.

[0132] The turnover dehumidification path 4 refers to the movement trajectory of the dehumidifier 3 during turnover dehumidification within the initial dehumidification range.

[0133] The cyclic dehumidification path 4 is generated using a path planning algorithm. This algorithm plans the cyclic dehumidification path based on the geometric characteristics of the initial dehumidification range and the principle of optimal coverage. The path planning algorithm adopts classic path planning methods such as the A* algorithm or genetic algorithm. The specific algorithm selection and parameter settings are determined by those skilled in the art based on the characteristics of the dehumidification equipment and the site layout, and will not be elaborated here.

[0134] S62: Control the dehumidifier 3 to perform circulating air supply according to the circulating dehumidification path 4, and collect real-time humidity distribution data during the circulating air supply process.

[0135] Real-time humidity distribution data refers to a series of humidity monitoring values ​​collected in real time by the onboard humidity sensor when the dehumidifier 3 moves along the dehumidification path 4.

[0136] Real-time humidity distribution data is obtained through continuous monitoring during the movement of the dehumidifier 3.

[0137] While controlling the dehumidifier 3 to circulate and supply air according to the circulation dehumidification path 4, it is necessary to collect real-time humidity distribution data during the circulation and air supply process for subsequent steps.

[0138] S63: Combine real-time humidity distribution data and turnover dehumidification path 4 to generate dynamic dehumidification range.

[0139] The dynamic dehumidification range refers to the actual dehumidification area 5 that is dynamically adjusted based on real-time humidity monitoring results.

[0140] The dynamic dehumidification range is determined by a dynamic range calculation model. This model analyzes the humidity gradient changes in real-time humidity distribution data and, combined with the coverage information of the turnover dehumidification path 4, generates the updated boundary of the dehumidification area 5 through a spatial interpolation algorithm. The specific parameters of the dynamic range calculation model are set by those skilled in the art based on the characteristics of real-time environmental changes, and will not be elaborated here.

[0141] S64: Update the turnover dehumidification path 4 based on the dynamic dehumidification range, and control the dehumidifier 3 to perform precise zone dehumidification based on the updated turnover dehumidification path 4.

[0142] The turnover dehumidification path 4 is updated using a path replanning algorithm. This algorithm is based on the spatial characteristics of the dynamic dehumidification range and uses an improved A* algorithm to recalculate the optimal dehumidification path. The path replanning algorithm comprehensively considers path length, dehumidification efficiency, and energy consumption indicators. Its specific implementation method can be designed by those skilled in the art according to the real-time path optimization requirements, and will not be elaborated here.

[0143] Based on the updated turnover dehumidification path 4, the dehumidifier 3 is controlled to accurately dehumidify high humidity areas.

[0144] Also includes: S70: Collects regional image information of dehumidification zone 5.

[0145] Regional image information refers to the panoramic visual data of dehumidification zone 5.

[0146] Regional image information is obtained through camera capture.

[0147] S71: Obstacle distribution information is obtained by identifying the area image information.

[0148] Obstacle distribution information refers to the data set of spatial location, geometric dimensions, and distribution density of obstacles within dehumidification zone 5.

[0149] This study employs a deep learning-based object detection algorithm to identify obstacle entities in images. A 3D coordinate transformation model is used to convert the identified obstacles from the image coordinate system to the actual spatial coordinate system, obtaining the spatial location data of the obstacles. Point cloud data analysis techniques are used to process the 3D spatial data of the obstacles, calculating their geometric dimensions. Finally, a spatial grid statistical method is used to analyze the distribution density of obstacles within the dehumidification area 5, thus obtaining obstacle distribution information. The object detection algorithm, 3D coordinate transformation model, point cloud data analysis technique, and spatial grid statistical method are all well-known concepts in the fields of machine vision and spatial modeling, and will not be elaborated upon here.

[0150] S72: Determine obstacle contour features based on obstacle distribution information.

[0151] Obstacle contour features refer to the set of characteristic parameters that describe the geometric characteristics of an obstacle's shape.

[0152] The obstacle contour features are obtained by extracting the boundary contours of obstacles using edge detection algorithms based on the spatial location and geometric dimensions data in the obstacle distribution information. The edge detection algorithm is common knowledge to those skilled in the art and will not be elaborated upon here.

[0153] S73: Combine obstacle contour features and real-time humidity distribution data to generate an obstacle avoidance and dehumidification path.

[0154] Obstacle avoidance dehumidification path refers to the optimal movement trajectory that avoids all obstacles while optimizing coverage of high humidity areas.

[0155] An environmental map is constructed using a grid model based on obstacle contour features, marking the areas occupied by obstacles. High-humidity areas are weighted within the grid model using real-time humidity distribution data. An A-path planning algorithm is then employed to prioritize passing through high-humidity weighted areas while ensuring a safe distance from obstacles, generating the optimal obstacle avoidance and dehumidification path. The grid map modeling method and the A-path planning algorithm are well-known principles in the field of mobile robot path planning and will not be elaborated upon here.

[0156] S74: Calculate the optimal air supply parameters based on the obstacle avoidance dehumidification path.

[0157] The optimal air supply parameters refer to the combination of air supply control parameters that achieve the best dehumidification effect.

[0158] Based on the curvature characteristics and path point spacing of the obstacle avoidance and dehumidification path, the baseline air supply angle for each path point is calculated using a kinematic model. Combining the humidity gradient values ​​from real-time humidity distribution data, the required air supply intensity is determined using a humidity response model. Based on the minimum bounding rectangle size in the obstacle contour features, air supply and obstacle avoidance parameters are calculated using a flow field simulation model. Finally, by integrating the baseline air supply angle, air supply intensity, and obstacle avoidance parameters, the optimal air supply parameter combination is generated using a parameter optimization algorithm. The kinematic model, humidity response model, flow field simulation model, and parameter optimization algorithm are all common knowledge in the field of fluid mechanics and control optimization, and will not be elaborated upon here.

[0159] S75: Controls dehumidifier 3 to dehumidify according to the obstacle avoidance dehumidification path, and adjusts the air supply direction and air supply intensity based on the optimal air supply parameters.

[0160] After obtaining the obstacle avoidance dehumidification path and the optimal air supply parameters, the dehumidifier 3 needs to be controlled to dehumidify according to the obstacle avoidance dehumidification path. At the same time, the air supply direction and air supply intensity are adjusted based on the optimal air supply parameters, so as to achieve precise and efficient dehumidification of high humidity areas while avoiding obstacles.

[0161] Also includes: S80: Collect current ambient wind parameters.

[0162] The current environmental wind parameters refer to the wind force and direction data of the external environment of dehumidification zone 5.

[0163] The current environmental wind parameters are obtained through wind speed and direction sensors.

[0164] S81: Calculate the environmental wind influence factor based on environmental wind parameters and obstacle avoidance dehumidification path.

[0165] The environmental wind impact factor is a quantitative indicator of the degree of influence of environmental wind on the air delivery effect of dehumidifier 3.

[0166] The environmental wind impact factor was calculated using an environmental wind interference assessment model. This model is based on wind speed and direction data in the environmental wind parameters, combined with the spatial orientation characteristics of the obstacle avoidance dehumidification path. It uses computational fluid dynamics simulation to analyze the interaction between the environmental wind and the airflow of the dehumidifier 3, quantifying the degree of influence of the environmental wind on the air delivery effect.

[0167] The specific calculation process includes: establishing a coupled model of the environmental wind field and the supply air jet, and analyzing the flow field distribution after their superposition; calculating the rate of change of the effective coverage area of ​​the supply air based on the flow field simulation results; and generating environmental wind influence factor values ​​through a weighted evaluation algorithm, taking into account factors such as wind speed, wind direction angle, and relative path position. The environmental wind interference assessment model and the weighted evaluation algorithm are common knowledge in the fields of fluid mechanics and environmental engineering, and will not be elaborated upon here.

[0168] S82: Adjust the optimal air supply parameters based on the environmental wind influence factor.

[0169] The correction process is implemented through an adaptive air supply parameter algorithm. This algorithm dynamically compensates for the air supply angle and intensity in the optimal air supply parameters based on the magnitude and direction of the environmental wind influence factor. The specific compensation strategy of the adaptive air supply parameter algorithm is designed by those skilled in the art based on the wind field interference characteristics, and will not be elaborated here.

[0170] S83: Adjust the air supply direction and air supply intensity based on the corrected optimal air supply parameters.

[0171] After the optimal air supply parameters are corrected, the air supply direction and intensity need to be adjusted based on the corrected optimal air supply parameters. The adjustment process is executed through the air supply control system, which adjusts the angle of the air supply mechanism and the fan speed in real time according to the corrected optimal air supply parameters to ensure that the expected air supply effect can still be maintained under environmental wind interference.

[0172] Also includes: S90: Generate air guide plate control parameters based on the obstacle avoidance and dehumidification path and the outline features of the obstacles.

[0173] The air guide plate control parameters refer to the key parameters that control the movement of the air guide plate, including the deployment angle, deflection direction, and deployment sequence.

[0174] The control parameters of the air guide plate are generated by the air guide plate parameter optimization algorithm. This algorithm is based on the spatial coordinate sequence of the obstacle avoidance and dehumidification path and the three-dimensional geometric data of the obstacle contour features. It calculates the optimal air guide plate configuration at each path point through airflow dynamics simulation.

[0175] Specifically, this includes: determining the deployment angle of the air guide vane based on the relative positional relationship between the path point and the obstacle; calculating the deflection direction of the air guide vane based on the geometric envelope surface of the obstacle's contour features; and planning the deployment sequence of the air guide vane according to the path movement speed. The air guide vane parameter optimization algorithm and the airflow dynamics simulation method are common knowledge in the fields of fluid mechanics and mechanical control, and will not be elaborated upon here.

[0176] S91: The air guide plate preset on the dehumidifier 3 is deployed based on the air guide plate control parameters.

[0177] An air guide plate is a mechanical device installed at the air outlet of the dehumidifier 3 to guide the direction of airflow.

[0178] Once the air guide plate control parameters are obtained, the air guide plate on dehumidifier 3 needs to be unfolded for subsequent steps.

[0179] S92: Collect ambient wind force, ambient wind direction, and ambient wind turbulence intensity.

[0180] Environmental wind force refers to the intensity value of environmental wind, and environmental wind direction refers to the direction in which the environmental wind flows.

[0181] Environmental wind turbulence intensity refers to the instantaneous fluctuation intensity of environmental wind speed, and is used to characterize the stability of the wind field.

[0182] The ambient wind force and direction are collected by wind speed and direction sensors.

[0183] The intensity of environmental wind turbulence is obtained by calculating the standard deviation of wind speed data per unit time. The specific calculation period is determined by those skilled in the art based on the required measurement accuracy, and will not be elaborated here.

[0184] S93: Combine ambient wind force, ambient wind direction, ambient wind turbulence intensity, and wind deflector control parameters to correct the wind deflector control parameters.

[0185] The correction process is implemented through an environmental wind compensation control algorithm. The algorithm first queries a preset wind angle correction coefficient table based on the magnitude of the environmental wind force to obtain the corresponding deployment angle compensation coefficient; then it calculates the angle between the environmental wind direction and the current air supply direction, and determines the compensation angle of the deflection direction by querying a wind direction deflection correction table; at the same time, based on the environmental wind turbulence intensity characteristics, it dynamically adjusts the deployment timing by querying a turbulence timing adjustment table.

[0186] The table of wind angle correction coefficients records the compensation coefficients for the deployment angle of the wind deflector corresponding to different wind speed ranges.

[0187] The wind deflection correction table records the deflection compensation angles corresponding to different angles between the ambient wind direction and the supply wind direction.

[0188] The turbulence timing adjustment table records the timing adjustment parameters corresponding to different turbulence intensity levels, including timing advance or delay. For example, the timing remains unchanged for low turbulence intensity, the timing is advanced by 50ms for medium turbulence intensity, and the timing is advanced by 100ms for high turbulence intensity.

[0189] The wind angle correction coefficient table, wind direction deflection correction table, and turbulence timing adjustment table were all pre-established by those skilled in the art using wind tunnel test data. The specific implementation method of the environmental wind compensation control algorithm is common knowledge in the field of intelligent control and will not be elaborated here.

[0190] S94: Adjust the deployment angle and deflection direction of the air guide plate based on the corrected air guide plate control parameters.

[0191] After the control parameters of the air guide plate are corrected, the deployment angle and deflection direction of the air guide plate need to be adjusted according to the corrected control parameters in order to actively compensate for environmental wind interference and dynamically maintain the best airflow guidance effect.

[0192] Based on the same inventive concept, embodiments of the present invention provide a mild hybrid energy-saving dehumidifier control system, comprising: The data acquisition module is used to collect information on condensation heat, inlet temperature, outlet temperature, supply air temperature, supply air humidity, availability status, target air temperature, supply air temperature, area humidity, real-time humidity distribution data, area image information, current ambient wind parameters, ambient wind force, ambient wind direction, and ambient wind turbulence intensity. A memory for storing a program that implements a mild hybrid energy-saving dehumidifier control method; The processor is used to load and execute programs stored in memory.

[0193] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional modules is used as an example. In practical applications, the above functions can be assigned to different functional modules as needed, that is, the internal structure of the device can be divided into different functional modules to complete all or part of the functions described above. The specific working process of the system, device, and unit described above can be referred to the corresponding process in the foregoing method embodiments, and will not be repeated here.

[0194] The above description is merely a preferred embodiment of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principles of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. A control method for a mild hybrid energy-saving dehumidifier, characterized in that, include: Collect preset information on the condensation heat of the air supply cooling system and the inlet temperature of the regenerated air; Heat recovery characteristics are extracted based on condensation heat information, and combined with inlet temperature information to determine the system thermal state; The regenerative heating mode is determined based on the system's thermal state; Collect preset outlet temperature data of the regenerative preheater; Based on the condensation heat information and outlet temperature data, determine whether the heat recovery meets the preheating requirements; When heat recovery does not meet the preheating requirements, a preset compensation heater is activated to heat the regenerated air based on the regeneration heating mode.

2. The control method for a mild hybrid energy-saving dehumidifier according to claim 1, characterized in that, The regenerative heating mode includes a mild hybrid energy-saving mode and a conventional heating mode. The mild hybrid energy-saving mode includes: Collect supply air temperature and humidity parameters; The characteristics of the supply air cooling load are obtained based on the supply air temperature and humidity parameters. The heat recovery power is determined by combining the characteristics of the supply air cooling load and the information on condensation heat. Configure preheating parameters based on heat recovery power and inlet temperature information; The preheating operation of the preheating preheater is controlled based on the preheating parameters.

3. The control method for a mild hybrid energy-saving dehumidifier according to claim 2, characterized in that, The conventional heating modes include: Collect available state parameters of high-grade heat sources and target air temperature of regenerated air; The temperature difference is obtained by matching the preset regeneration temperature value with the system thermal state. The compensation heating amount is matched based on the temperature difference; Based on available state parameters and compensation heating amount, generate compensation heating command; In response to a compensation heating command, a preset compensation heater is controlled to heat the preheated regenerated air until the target air temperature is reached.

4. The control method for a mild hybrid energy-saving dehumidifier according to claim 1, characterized in that, Also includes: Collect the temperature of the supplied air; The supply air temperature difference is determined based on the supply air temperature and the preset target supply air temperature. Determine whether the supply air temperature difference exceeds the preset temperature difference threshold; When the supply air temperature difference exceeds the temperature difference threshold, the preset precooler is activated to absorb the heat of the supply air. When the supply air temperature difference does not exceed the temperature difference threshold, the preset precooler is kept off.

5. The control method for a mild hybrid energy-saving dehumidifier according to claim 1, characterized in that, Also includes: Collect the humidity information of the preset dehumidification area (5); Determine humidity distribution characteristics based on regional humidity information; Based on the humidity distribution characteristics, the area with the highest humidity was determined (6); Control the dehumidifier (3) to perform dehumidification on the area (6) with the highest humidity using a preset dehumidification method.

6. The control method for a mild hybrid energy-saving dehumidifier according to claim 5, characterized in that, The dehumidification method includes: The initial dehumidification range is determined based on the area with the highest humidity (6); Based on the initial dehumidification range, the turnover dehumidification path is obtained (4); Control the dehumidifier (3) to carry out air circulation according to the circulation dehumidification path (4), and collect real-time humidity distribution data during the circulation air circulation process; Combine real-time humidity distribution data and turnover dehumidification path (4) to generate dynamic dehumidification range; Based on the dynamic dehumidification range, the turnover dehumidification path (4) is updated, and based on the updated turnover dehumidification path (4), the dehumidifier (3) is controlled to perform precise regional dehumidification.

7. The control method for a mild hybrid energy-saving dehumidifier according to claim 6, characterized in that, Also includes: Collect regional image information of the dehumidification area (5); Obstacle distribution information is obtained by identifying regional image information; Obstacle contour features are determined based on obstacle distribution information; The obstacle avoidance and dehumidification path is generated by combining obstacle outline features and real-time humidity distribution data. Optimal air supply parameters are calculated based on the obstacle avoidance and dehumidification path. Control the dehumidifier (3) to dehumidify according to the obstacle avoidance dehumidification path, and at the same time adjust the air supply direction and air supply intensity based on the optimal air supply parameters.

8. The control method for a mild hybrid energy-saving dehumidifier according to claim 7, characterized in that, Also includes: Collect current environmental wind parameters; The environmental wind influencing factor is calculated based on environmental wind parameters and obstacle avoidance and dehumidification paths. The optimal air supply parameters are adjusted based on environmental wind influencing factors. Adjust the air supply direction and intensity based on the corrected optimal air supply parameters.

9. The control method for a mild hybrid energy-saving dehumidifier according to claim 7, characterized in that, Also includes: The control parameters for the air guide plate are generated based on the obstacle avoidance and dehumidification path and the outline features of the obstacles. The air guide plate, which is pre-set on the dehumidifier (3), is deployed based on the air guide plate control parameters. Collect ambient wind force, ambient wind direction, and ambient wind turbulence intensity; The control parameters of the wind deflector are corrected by combining the ambient wind force, ambient wind direction, ambient wind turbulence intensity, and wind deflector control parameters. Adjust the deployment angle and deflection direction of the air guide plate based on the revised control parameters.

10. A mild hybrid energy-saving dehumidifier control system, characterized in that, include: The data acquisition module is used to collect information on condensation heat, inlet temperature, and outlet temperature. A memory for storing a program that implements a mild hybrid energy-saving dehumidifier control method as described in any one of claims 1 to 9; The processor is used to load and execute programs stored in memory.

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