Dehumidifying apparatus and control method thereof

Abstract

The application provides a dehumidification device and a control method thereof. The method comprises the following steps: obtaining the inlet temperature and humidity of process air, a target supply air dew point, a process air flow rate, air states before and after a first-stage rotary wheel, air states before and after a second-stage rotary wheel, a first-stage regeneration air state, a second-stage regeneration air state, and node states of a low-temperature cold supply node, a medium-temperature heat absorption node, a medium-temperature heat supply node, and a high-temperature heat supply node; determining a process air pre-cooling load, an intermediate cooling load, a first-stage rotary wheel dehumidification load, and a second-stage rotary wheel dehumidification load according to the inlet temperature and humidity of process air, the target supply air dew point, the process air flow rate, the air states before and after the first-stage rotary wheel, and the air states before and after the second-stage rotary wheel; determining a first-stage regeneration heat load according to the first-stage rotary wheel dehumidification load and the first-stage regeneration air state, and determining a second-stage regeneration heat load according to the second-stage rotary wheel dehumidification load and the second-stage regeneration air state. The above technical scheme can improve the reliability, energy saving, and control accuracy of the dehumidification process.

Description

Technical Field

[0001] This invention relates to the field of dehumidification control technology, and in particular to a dehumidification device and its control method. Background Technology

[0002] Rotary dehumidification technology is an important technical approach for achieving deep dehumidification and low dew point air environments. Its basic principle is to utilize solid adsorbent materials such as silica gel, molecular sieves, and composite adsorbents to adsorb water molecules in the air, thereby reducing the moisture content of the treated air. For applications such as lithium battery manufacturing, electronic cleanrooms, pharmaceutical production, and low dew point storage, which typically require supply air with a low dew point, single-stage rotary dehumidification systems are often insufficient to reliably meet deep dehumidification needs. Therefore, two-stage rotary dehumidification systems are frequently used in engineering projects.

[0003] Currently, a two-stage rotary dehumidification system typically includes a pre-cooling section for processed air, a primary rotary dehumidification section, an intermediate cooling section, a secondary rotary dehumidification section, and a rotary regeneration section. After pre-cooling, the processed air enters the primary rotary dehumidifier for main dehumidification, and then, after intermediate cooling, enters the secondary rotary dehumidifier for fine dehumidification. Simultaneously, regeneration air, heated by steam, electricity, or gas-fired hot air, passes through the rotary regeneration zone, causing the adsorbent to desorb moisture and restore its moisture absorption capacity.

[0004] However, the dehumidification process of current two-stage rotary dehumidification systems still needs improvement. Summary of the Invention

[0005] This invention provides a dehumidification device and its control method, which can improve the reliability, energy efficiency and control accuracy of the dehumidification process.

[0006] To achieve the above objectives, the present disclosure provides the following technical solutions.

[0007] A control method for a dehumidification device, the dehumidification device comprising: a cascade combined cooling and heating unit and a two-stage rotary dehumidification system, the two-stage rotary dehumidification system comprising a processing air flow path, a first-stage rotary wheel, a second-stage rotary wheel, a first-stage regeneration air flow path, and a second-stage regeneration air flow path, the processing air flow path comprising a precooling section, a first-stage rotary wheel processing area, an intermediate cooling section, and a second-stage rotary wheel processing area arranged sequentially along the processing air flow direction, the cascade combined cooling and heating unit forming a low-temperature cooling node, a medium-temperature heat absorption node, a medium-temperature heating node, and a high-temperature heating node, the control method comprising: Step A: Obtain the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air status before and after the first-stage impeller, the air status before and after the second-stage impeller, the air status of the first-stage regenerated air, the air status of the second-stage regenerated air, and the node status of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node. Step B: Determine the pre-cooling load, intermediate cooling load, first-stage dehumidification load, and second-stage dehumidification load of the processed air based on the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air conditions before and after the first-stage impeller, and the air conditions before and after the second-stage impeller. Step C: Determine the primary regeneration heat load based on the primary dehumidification load and the primary regeneration air state, and determine the secondary regeneration heat load based on the secondary dehumidification load and the secondary regeneration air state; Step D involves controlling the low-temperature cooling node to provide cooling capacity to the pre-cooling section, controlling the medium-temperature heat absorption node to provide heat absorption capacity to the intermediate cooling section, controlling the medium-temperature heating node to provide heat to the secondary regeneration air flow path, and controlling the high-temperature heating node to provide heat to the primary regeneration air flow path. This includes: determining the target cooling state of the low-temperature cooling node based on the pre-cooling load of the processed air, and adjusting the evaporation temperature, refrigerant flow rate, and / or low-temperature compressor frequency of the low-temperature cooling node to ensure that the outlet air state of the pre-cooling section reaches the pre-cooling target; determining the target heat absorption state of the medium-temperature heat absorption node based on the intermediate cooling load, and adjusting the heat absorption temperature and heat exchange medium of the medium-temperature heat absorption node. The flow rate and / or the heat absorbed by the high-temperature stage evaporator are adjusted to ensure that the outlet air condition of the intermediate cooling section reaches the intermediate cooling target. The target heating state of the medium-temperature heating node is determined based on the secondary regeneration heat load, and the heating temperature, heat medium flow rate, and / or the low-temperature stage condensation heat distribution ratio of the medium-temperature heating node are adjusted to ensure that the secondary regeneration airflow path reaches the secondary regeneration target. The target heating state of the high-temperature heating node is determined based on the primary regeneration heat load, and the heating temperature, heat medium flow rate, and / or the high-temperature stage compressor frequency of the high-temperature heating node are adjusted to ensure that the primary regeneration airflow path reaches the primary regeneration target. The heating temperature of the high-temperature heating node is higher than that of the medium-temperature heating node. Step E involves driving the primary regeneration airflow path and the secondary regeneration airflow path to operate independently, and adjusting them respectively according to the primary regeneration heat load and the secondary regeneration heat load; Step F: Based on the target air supply dew point, the air state after the secondary rotor, and the node states of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node, the actual air supply dew point is made to approach the target air supply dew point.

[0008] A dehumidification device, comprising: A cascade combined cooling and heating unit includes a low-temperature stage cycle, a high-temperature stage cycle, and an interstage heat exchange unit disposed between the low-temperature stage cycle and the high-temperature stage cycle; A two-stage rotary dehumidification system includes a treatment airflow path, a primary rotary wheel, a secondary rotary wheel, a primary regeneration airflow path, and a secondary regeneration airflow path. The treatment airflow path includes a precooling section, a primary rotary wheel treatment area, an intermediate cooling section, and a secondary rotary wheel treatment area arranged sequentially along the treatment airflow direction. The primary regeneration airflow path is connected to the regeneration area of ​​the primary rotary wheel, and the secondary regeneration airflow path is connected to the regeneration area of ​​the secondary rotary wheel. The primary regeneration airflow path and the secondary regeneration airflow path are independent of each other. The low-temperature cooling node is connected to the pre-cooling section for heat exchange; the medium-temperature heat absorption node is connected to the intermediate cooling section for heat exchange; the medium-temperature heating node is connected to the secondary regenerated air flow path for heat exchange; and the high-temperature heating node is connected to the primary regenerated air flow path for heat exchange. The controller is connected to the cascade combined cooling and heating unit, the primary regenerative airflow path, the secondary regenerative airflow path, the primary impeller, and the secondary impeller, and is configured to execute the control method described in any of the foregoing embodiments.

[0009] The above-mentioned cascade combined cooling and heating unit and the two-stage rotary dehumidifier system work together to comprehensively understand the operating conditions of the processed air side, the regenerated air side, and the cold and heat source side by acquiring the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air state before and after each stage of the rotary dehumidifier, the regenerated air state, and the state of each cold and heat node. Based on this, the pre-cooling load, intermediate cooling load, first-stage rotary dehumidifier load, and second-stage rotary dehumidifier load of the processed air are determined according to the air state and the target supply air dew point. This enables accurate identification of the load demand in the dehumidification process and avoids energy waste and dew point fluctuations caused by insufficient or excessive supply of cold and heat. Furthermore, the corresponding regeneration heat load is determined according to the first-stage and second-stage rotary dehumidifier loads, and the medium-temperature heating node and the high-temperature heating node are controlled to supply heat to the second-stage regenerated air flow path and the first-stage regenerated air flow path, respectively. This ensures that the regeneration demand of different dehumidification stages can be matched with the corresponding temperature heat source, thereby improving the thermal energy utilization efficiency. After entering the operation and adjustment phase, the primary and secondary regeneration airflow paths are driven to operate independently and adjusted according to their respective regeneration heat loads. This allows the two-stage rotary dehumidification system to perform differentiated control based on the moisture absorption state and regeneration requirements of different stages of the rotary dehumidifier, avoiding mutual interference between the two regeneration processes. Simultaneously, by combining the target supply air dew point, the air state after the secondary rotary dehumidifier, and the node states of low-temperature cooling nodes, medium-temperature heat absorption nodes, medium-temperature heating nodes, and high-temperature heating nodes, the cooling, heat absorption, and heating capacities are coordinated and adjusted to ensure that the actual supply air dew point approaches the target supply air dew point, achieving continuous and stable control of supply air quality. This method constructs a deep collaborative control scheme that integrates load identification, cooling and heating matching, independent regeneration, and dew point feedback, improving the reliability, energy efficiency, and control accuracy of the dehumidification process. Attached Figure Description

[0010] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0011] Figure 1 This is a flowchart of a control method for a dehumidification device according to an embodiment of this application; Figure 2 This is a schematic diagram of the structure of a dehumidification device according to an embodiment of this application; Figure 3 This is a comparison chart of system operating energy consumption in one embodiment of this application. Detailed Implementation

[0012] The following detailed description of preferred embodiments is a preferred mode for carrying out the invention. This description is not intended to be limiting; it is provided to illustrate the general principles of the invention.

[0013] It should be understood that, for ease of understanding of the present invention, the terms "installation," "connection," "coupling," and "installation" in the following description refer to the connection relationships shown in the drawings. For example, "connection" can refer to a permanent connection or a detachable connection. Furthermore, "connection" can also refer to a direct connection or an indirect connection, or a connection via other auxiliary components. Therefore, the above terms should not be construed as limiting the actual connections of the various elements of the present invention.

[0014] It should be understood that the terms "first," "second," "an," "a," and "one" in the following description refer to "at least one" or "one or more" in the embodiments. In particular, the term "a" may refer to "one" in one embodiment and "more than one" in another embodiment. Therefore, the above terms should not be construed as limiting the actual number of elements of the present invention.

[0015] To facilitate understanding of the present invention, a more complete description will be given below with reference to the accompanying drawings. Preferred embodiments of the invention are shown in the drawings. However, the invention can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided to provide a thorough and complete understanding of the disclosure of the invention.

[0016] As described in the background section, the dehumidification process of current two-stage rotary dehumidification systems still needs improvement, specifically in the following aspects: First, rotary regeneration heat sources typically rely on high-grade energy sources such as steam, electric heating, or gas-fired hot air, resulting in high investment in supporting systems and high energy consumption during operation.

[0017] Second, air precooling and rotor regeneration are usually handled independently by the refrigeration system and the heating system, respectively. The condensation heat of the refrigeration system is not effectively coupled with the heat demand of rotor regeneration, resulting in problems of heat emission and insufficient energy cascade utilization.

[0018] Third, the dehumidification load, regeneration temperature, regeneration air volume and rotor speed requirements of the first-stage and second-stage rotors are different. If a unified regeneration air path or simple linkage control is adopted, it is difficult to balance the main dehumidification capacity and low dew point stability.

[0019] Fourth, the rotary adsorption process releases adsorption heat, raising the temperature of the processed air, requiring a stable cooling capacity in the intermediate cooling section. Existing systems lack synergistic utilization of the heat released by rotary adsorption and the intermediate cooling load with the heat pump cycle.

[0020] Fifth, although cascade combined cooling and heating units can provide cooling and heating at different temperatures, there is still a lack of complete solutions in the existing technology for how to achieve four-temperature matching, low-temperature stage condensate heat diversion, independent control of dual regeneration air paths, and dew point closed-loop control between them and the two-stage rotary dehumidification system.

[0021] Therefore, in order to solve at least one of the above technical problems, it is necessary to provide a device and control method that can couple multiple cold and hot nodes of a cascade combined cooling and heating unit with the pre-cooling, intermediate cooling, primary regeneration and secondary regeneration processes of a two-stage rotary dehumidifier system, so as to reduce the dependence on traditional steam or electric heating, improve the overall energy efficiency of the system, and ensure the stability of low dew point air supply.

[0022] In other words, this application embodiment achieves full-chain operation optimization from the processed air side to the regenerated air side, from the supply of cold and heat sources to the dehumidification demand of the rotary dehumidifier, and from single-point control to multi-node collaboration through staged closed-loop control of "state perception, load analysis, cold and heat coordination, independent regeneration, and dew point closed loop". This method elevates the traditional dehumidification control that relies on fixed operating parameters or single dew point feedback to a dynamic decision-making process based on the fusion of multi-source air states, graded dehumidification loads, and cascaded cold and heat node states. It forms an intelligent dehumidification control mechanism that can adapt to inlet air conditions, target supply air dew point, and cold and heat source operating states, significantly improving the operational stability, energy utilization efficiency, and supply air dew point control reliability of the dehumidification device.

[0023] To enable those skilled in the art to better understand and implement this solution, the following detailed description of the specific solution, principles, advantages, and effects of the present invention is provided with reference to the accompanying drawings and specific embodiments.

[0024] See Figure 1 and Figure 2 , Figure 1 This is a flowchart of a control method for a dehumidification device according to an embodiment of this application. Figure 2This is a schematic diagram of the structure of a dehumidification device according to an embodiment of this application.

[0025] like Figure 2 As shown, the dehumidification device 100 may include: a cascade combined cooling and heating unit 300 and a two-stage rotary dehumidification system 200.

[0026] The dual-stage rotary dehumidification system 200 includes a processing air flow path 210, a first-stage rotary wheel 214, a second-stage rotary wheel 218, a first-stage regeneration air flow path (not shown in the figure), and a second-stage regeneration air flow path (not shown in the figure). The processing air flow path includes a pre-cooling section 213, a first-stage rotary wheel processing area (i.e., the area between the first-stage rotary wheel 214 and the intermediate cooling section 216), an intermediate cooling section 216, and a second-stage rotary wheel processing area (i.e., the area between the second-stage rotary wheel 218 and the post-heating section 220) arranged sequentially along the processing air flow direction.

[0027] The cascade combined cooling and heating unit 300 forms a low-temperature cooling node C1, a medium-temperature heat absorption node C2, a medium-temperature heating node H1, and a high-temperature heating node H2.

[0028] It should be noted that the air flow path 210 is also provided with an air inlet 211, a first filter 212, a second filter 217 and a third filter 221; and a first fan 215 disposed between the first filter 212 and the first stage rotor 214, and a second fan 219 disposed between the second stage rotor 218 and the afterheating section 220.

[0029] Accordingly, the control methods include: Step A: Obtain the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air status before and after the first-stage impeller, the air status before and after the second-stage impeller, the air status of the first-stage regenerated air, the air status of the second-stage regenerated air, and the node status of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node.

[0030] In some embodiments, during the operation of the two-stage rotary dehumidifier system, the controller acquires the above parameters to perform dehumidification adjustment.

[0031] Specifically, the processed air inlet temperature and humidity can include the processed air inlet temperature and the processed air inlet relative humidity. The processed air flow rate can be either the processed air mass flow rate or the processed air volume flow rate. When the volume flow rate is obtained, the controller can convert it into mass flow rate based on the air density.

[0032] The air conditions before and after the first-stage rotor may include the air temperature at the inlet of the first-stage rotor, the relative humidity at the inlet of the first-stage rotor, the air temperature at the outlet of the first-stage rotor, and the relative humidity at the outlet of the first-stage rotor, or the moisture content of the air before and after the first-stage rotor calculated from the above parameters.

[0033] The air conditions before and after the secondary rotor can include the inlet air temperature, relative humidity, outlet air temperature, relative humidity, and dew point. Since the outlet air of the secondary rotor is the supply air or nearly the supply air, the dew point of the outlet air can be used as the actual supply air dew point.

[0034] The primary regenerated air status can include the primary regenerated air inlet temperature, primary regenerated air outlet temperature, primary regenerated air flow rate, and primary regenerated air humidity. The secondary regenerated air status can include the secondary regenerated air inlet temperature, secondary regenerated air outlet temperature, secondary regenerated air flow rate, and secondary regenerated air humidity.

[0035] The node status of low-temperature cooling nodes, medium-temperature heat absorption nodes, medium-temperature heating nodes, and high-temperature heating nodes can include the inlet temperature, outlet temperature, heat exchange medium flow rate, pressure, heat exchange capacity, or available heat exchange capacity of the corresponding node.

[0036] As a non-limiting example, the node status of a low-temperature cooling node may include refrigerant inlet temperature, refrigerant outlet temperature, and refrigerant flow rate; the node status of a high-temperature heating node may include heat medium inlet temperature, heat medium outlet temperature, and heat medium flow rate.

[0037] It should be noted that not all of the above operating states need to be used as control parameters simultaneously. In actual control, a subset of parameters can be selected as the basis for control, depending on factors such as control accuracy, sensor configuration, and equipment cost.

[0038] Step B: Based on the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air conditions before and after the first-stage impeller and the air conditions before and after the second-stage impeller, determine the processed air pre-cooling load, intermediate cooling load, first-stage impeller dehumidification load and second-stage impeller dehumidification load.

[0039] In some embodiments, the controller determines the pre-cooling load, intermediate cooling load, first-stage dehumidification load, and second-stage dehumidification load of the processed air based on the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air conditions before and after the first-stage impeller, and the air conditions before and after the second-stage impeller.

[0040] In this embodiment, the pre-cooling load of the processed air represents the cooling capacity required by the low-temperature cooling node for the pre-cooling section. The intermediate cooling load represents the heat absorption capacity required by the medium-temperature heat absorption node for the intermediate cooling section. The first-stage dehumidification load represents the amount of moisture that the first-stage rotor needs to adsorb. The second-stage dehumidification load represents the amount of moisture that the second-stage rotor needs to further adsorb.

[0041] As a non-limiting example, the controller can determine the total dehumidification load based on the difference between the moisture content of the processed air inlet and the target supply air moisture content, and then allocate the total dehumidification load to the first-stage and second-stage impellers according to the principle that the first-stage impeller bears the main dehumidification load and the second-stage impeller bears the fine dehumidification load.

[0042] In some embodiments, processing the air inlet temperature and humidity includes processing the air inlet temperature and processing the air inlet relative humidity.

[0043] Accordingly, step B may include: Step B1: Calculate the moisture content of the processed air inlet based on the processed air inlet temperature and the processed air inlet relative humidity.

[0044] As one implementation method, the controller can first determine the saturated water vapor pressure at the inlet temperature of the processed air, then calculate the water vapor partial pressure based on the relative humidity of the inlet of the processed air, and finally calculate the moisture content of the inlet of the processed air based on the water vapor partial pressure and atmospheric pressure.

[0045] As another implementation method, the controller can call the pre-stored humid air state table or enthalpy-humidity diagram data, and look up the table to obtain the moisture content of the processed air inlet based on the processed air inlet temperature and the processed air inlet relative humidity.

[0046] Step B2: Calculate the target supply air moisture content based on the target supply air dew point.

[0047] In some embodiments, the target supply air dew point corresponds to the partial pressure of water vapor in the target supply air. The controller can determine the target water vapor partial pressure based on the target supply air dew point and further calculate the target supply air moisture content.

[0048] In this embodiment, the target air supply dew point can be set by the user or sent by the host computer, cleanroom control system, or process equipment.

[0049] As a non-limiting example, in a lithium battery drying room, the target supply air dew point can be set to -40°C, -50°C, or -60°C; in a general low-humidity cleanroom, the target supply air dew point can be set between -20°C and 40°C.

[0050] Step B3: Calculate the total dehumidification load based on the moisture content of the treated air inlet, the target supply air moisture content, and the treated air flow rate.

[0051] In some embodiments, the controller determines the amount of moisture to be removed per unit mass of air based on the difference between the moisture content of the processed air inlet and the target supply air moisture content, and then calculates the total dehumidification load in conjunction with the processed air flow rate.

[0052] As a non-limiting example, when the processed air mass flow rate is G, the inlet moisture content of the processed air is d_in, and the target supply air moisture content is d_tar, the total dehumidification load W can be expressed as: W = ρ × G × (d_in - d_tar), where ρ is the air density, which can be 1.2. When d_in is less than or equal to d_tar, it indicates that the inlet moisture content of the processed air is no higher than the target supply air moisture content, and the controller can reduce the regeneration intensity of the dehumidifier or enter a low-load energy-saving mode.

[0053] Step B4: Following the principle that the primary dehumidifier bears the main dehumidification load and the secondary dehumidifier bears the fine dehumidification load, the total dehumidification load is allocated to the initial values ​​of the primary dehumidifier dehumidification load and the secondary dehumidifier dehumidification load.

[0054] In some embodiments, the controller distributes the total dehumidification load to the initial values ​​of the dehumidification load of the first-stage rotor and the fine dehumidification load of the second-stage rotor, according to the principle that the first-stage rotor bears the main dehumidification load and the second-stage rotor bears the fine dehumidification load.

[0055] In this embodiment, the primary impeller is used to remove most of the moisture in the processed air, and the secondary impeller is used to further reduce the dew point of the processed air.

[0056] As a non-limiting example, 60% to 90% of the total dehumidification load can be allocated to the first-stage rotor, and 10% to 40% of the total dehumidification load can be allocated to the second-stage rotor. The specific proportions can be determined based on the rotor model, adsorbent material, target dew point, inlet air humidity, and operating experience.

[0057] For example, when the target supply air dew point is low, the load proportion undertaken by the secondary rotor can be increased; when the moisture content of the treated air inlet is high, the load proportion undertaken by the primary rotor can be increased.

[0058] Step B5: Calculate the difference in air humidity before and after the first-stage rotor based on the air conditions before and after the first-stage rotor, and correct the initial value of the first-stage rotor dehumidification load based on the difference in air humidity before and after the first-stage rotor to obtain the first-stage rotor dehumidification load.

[0059] In some embodiments, when the difference in humidity between the air before and after the primary rotor is lower than the target difference corresponding to the initial value of the primary rotor's dehumidification load, it indicates that the actual dehumidification capacity of the primary rotor is insufficient, and the controller will correct the primary rotor's dehumidification load upwards. This can be achieved by increasing the primary regeneration air temperature, increasing the primary regeneration air flow rate, or increasing the primary rotor speed.

[0060] When the difference in humidity between the air before and after the primary rotor is higher than the target difference corresponding to the initial value of the primary rotor's dehumidification load, it indicates that the actual dehumidification capacity of the primary rotor is sufficient, and the controller can adjust the primary rotor's dehumidification load downwards. This can be achieved by reducing the primary regeneration air temperature, reducing the primary regeneration air flow rate, or reducing the primary rotor speed.

[0061] With the above modifications, the dehumidification load of the first-stage rotor is no longer determined solely by the inlet status and target dew point, but is dynamically updated based on the actual operating performance of the first-stage rotor.

[0062] Step B6: Calculate the difference in air humidity before and after the secondary rotor based on the air conditions before and after the secondary rotor, and correct the initial value of the dehumidification load of the secondary rotor based on the difference in air humidity before and after the secondary rotor to obtain the dehumidification load of the secondary rotor.

[0063] In some embodiments, when the dew point of the air after the secondary impeller is higher than the target supply air dew point, the controller can still increase the dehumidification load of the secondary impeller even if the difference in air humidity before and after the secondary impeller reaches the initial set value, to ensure that the final supply air dew point meets the requirements. When the dew point of the air after the secondary impeller is lower than the target supply air dew point and remains stable, the controller can reduce the dehumidification load of the secondary impeller to reduce the regeneration energy consumption of the secondary impeller.

[0064] Step B7: Determine the pre-cooling load of the processed air based on the inlet temperature of the processed air, the target pre-cooling temperature, and the flow rate of the processed air.

[0065] In some embodiments, the target precooling temperature can be determined based on the target state of the primary rotor inlet. The controller calculates the sensible heat that needs to be removed in the precooling section based on the process air inlet temperature, the target precooling temperature, and the process air flow rate. If condensation dehumidification occurs during the precooling process, the latent heat cooling load can be further calculated based on the moisture content of the air at the inlet and outlet of the precooling section.

[0066] As a non-limiting example, when the processed air inlet temperature is higher than the target pre-cooling temperature, the controller increases the cooling capacity of the low-temperature cooling node; when the processed air inlet temperature is lower than the target pre-cooling temperature, the controller reduces the cooling capacity of the low-temperature cooling node or bypasses part of the processed air.

[0067] Step B8: Determine the intermediate cooling load based on the first-stage rotor outlet air temperature, the second-stage rotor inlet target temperature, and the processing air flow rate.

[0068] In some embodiments, the primary rotor releases adsorption heat when adsorbing moisture from the air, causing the outlet air temperature of the primary rotor to rise. To ensure the fine dehumidification capability of the secondary rotor, an intermediate cooling section is needed to cool the outlet air of the primary rotor to the target inlet temperature of the secondary rotor.

[0069] The controller determines the intermediate cooling load based on the primary rotor outlet air temperature, the secondary rotor inlet target temperature, and the processed air flow rate. The higher the primary rotor outlet air temperature, the lower the secondary rotor inlet target temperature, or the higher the processed air flow rate, the greater the intermediate cooling load.

[0070] By employing the above technical solution, the moisture content of the treated air inlet can be calculated based on the treated air inlet temperature and relative humidity, and the target supply air moisture content can be calculated based on the target supply air dew point. This allows the actual moisture content of the inlet air and the target supply air dew point requirement to be converted into controllable moisture content parameters. Consequently, the accuracy of determining the total dehumidification load, the first-stage dehumidification load, the second-stage dehumidification load, the precooling load, and the intermediate cooling load can be improved, providing a foundation for subsequent four-node matching control and reducing problems such as over-regeneration, under-regeneration, insufficient precooling, or insufficient intermediate cooling.

[0071] Step C: Determine the primary regeneration heat load based on the primary dehumidification load and the primary regeneration air state, and determine the secondary regeneration heat load based on the secondary dehumidification load and the secondary regeneration air state.

[0072] In some embodiments, the primary dehumidifier carries the main dehumidification load, and its water adsorption capacity is typically greater than that of the secondary dehumidifier; therefore, the primary regeneration heat load is usually larger. The secondary dehumidifier carries the fine dehumidification load, and its water adsorption capacity is typically smaller, but it has a more direct impact on the supply air dew point. Therefore, the secondary regeneration heat load needs to be dynamically adjusted based on the actual supply air dew point.

[0073] As a non-limiting example, when the humidity of the air at the outlet of the first-stage rotor increases, it indicates that the dehumidification capacity of the first-stage rotor is insufficient, and the controller can increase the heat load of the first-stage regeneration. When the dew point of the air at the outlet of the second-stage rotor is higher than the target supply air dew point, it indicates that the fine dehumidification capacity of the second-stage rotor is insufficient, and the controller can increase the heat load of the second-stage regeneration.

[0074] Step D: Control the low-temperature cooling node to provide cooling capacity to the pre-cooling section, control the medium-temperature heat absorption node to provide heat absorption capacity to the intermediate cooling section, control the medium-temperature heating node to provide heat to the secondary regeneration air flow path, and control the high-temperature heating node to provide heat to the primary regeneration air flow path.

[0075] In some embodiments, four hot and cold nodes are controlled to be matched in a cascade manner with a two-stage rotary dehumidification system.

[0076] Specifically, the low-temperature cooling node corresponds to the pre-cooling process of the treated air, the medium-temperature heat absorption node corresponds to the intermediate cooling process after the first-stage rotor, the medium-temperature heating node corresponds to the regeneration process of the second-stage rotor, and the high-temperature heating node corresponds to the regeneration process of the first-stage rotor. Thus, the low-temperature cooling capacity, medium-temperature heat absorption capacity, medium-temperature heating capacity, and high-temperature heating capacity of the cascade combined cooling and heating unit are respectively used to meet the different temperature zone requirements of the two-stage rotor dehumidification system.

[0077] In some embodiments, step D includes: Step D1: Determine the target cooling state of the low-temperature cooling node based on the pre-cooling load of the processed air, and adjust the evaporation temperature, refrigerant flow rate and / or low-temperature stage compressor frequency of the low-temperature cooling node so that the air state at the outlet of the pre-cooling section reaches the pre-cooling target.

[0078] In some embodiments, the target cooling state of the low-temperature cooling node is determined based on the pre-cooling load of the processed air.

[0079] Specifically, the cryogenic cooling node is used to provide cooling capacity to the pre-cooling section. The controller determines the target cooling state of the cryogenic cooling node based on the pre-cooling load of the processed air.

[0080] When the pre-cooling load increases, the controller can lower the evaporation temperature of the cryogenic cooling node, increase the refrigerant flow rate of the cryogenic cooling node, or increase the frequency of the cryogenic stage compressor. When the pre-cooling load decreases, the controller can raise the evaporation temperature of the cryogenic cooling node, decrease the refrigerant flow rate of the cryogenic cooling node, or decrease the frequency of the cryogenic stage compressor.

[0081] Step D2: Determine the target heat absorption state of the intermediate temperature heat absorption node based on the intermediate cooling load, and adjust the heat absorption temperature, heat exchange medium flow rate and / or heat absorption on the high temperature stage evaporation side of the intermediate temperature heat absorption node so that the air state at the outlet of the intermediate cooling section reaches the intermediate cooling target.

[0082] In some embodiments, the target heat absorption state of the intermediate temperature heat absorption node is determined based on the intermediate cooling load.

[0083] Specifically, the intermediate-temperature heat absorption node is used to provide heat absorption capacity to the intermediate cooling section. The controller determines the target heat absorption state of the intermediate-temperature heat absorption node based on the intermediate cooling load.

[0084] When the intermediate cooling load increases, the controller can lower the heat absorption temperature of the intermediate temperature heat absorption node, increase the flow rate of the heat exchange medium at the intermediate temperature heat absorption node, or increase the heat absorption on the evaporator side of the high-temperature stage. When the intermediate cooling load decreases, the controller can raise the heat absorption temperature of the intermediate temperature heat absorption node or lower the flow rate of the heat exchange medium at the intermediate temperature heat absorption node.

[0085] In some embodiments, the provision of heat absorption capacity from the intermediate temperature heat absorption node to the intermediate cooling section includes an intermediate temperature cooling correction process.

[0086] The intermediate-temperature cooling correction process includes: acquiring the air conditions at the outlet of the first-stage rotor, the air conditions at the outlet of the intermediate cooling section, the target inlet condition of the second-stage rotor, and the node conditions of the intermediate-temperature heat absorption node; determining the actual intermediate cooling load based on the air conditions at the outlet of the first-stage rotor, the air conditions at the outlet of the intermediate cooling section, and the processing air flow rate; determining the intermediate cooling deviation based on the target inlet condition of the second-stage rotor and the air conditions at the outlet of the intermediate cooling section; judging whether the intermediate-temperature heat absorption node can eliminate the intermediate cooling deviation based on the node conditions of the intermediate-temperature heat absorption node; when the intermediate-temperature heat absorption node can eliminate the intermediate cooling deviation, adjusting the heat exchange medium flow rate, heat absorption temperature, and / or the heat absorption on the evaporator side of the high-temperature stage of the intermediate-temperature heat absorption node; when the intermediate-temperature heat absorption node cannot eliminate the intermediate cooling deviation, reducing the heat absorption temperature of the intermediate-temperature heat absorption node, increasing the heat exchange capacity of the intermediate-temperature heat absorption node, calling upon the low-temperature cooling node to supplement the cooling of the intermediate cooling section, and / or reducing the processing air load entering the intermediate cooling section.

[0087] Specifically, the air exiting the first-stage rotor is cooled after entering the intermediate cooling section. The controller determines the actual sensible heat removed by the intermediate cooling section based on the first-stage rotor outlet air temperature, the intermediate cooling section outlet air temperature, and the processed air flow rate. If condensation and dehumidification also occur in the intermediate cooling section, the controller can also calculate the latent heat load based on the moisture content of the first-stage rotor outlet air and the intermediate cooling section outlet air.

[0088] The air outlet of the intermediate cooling section is the same as the air inlet of the secondary rotor. The controller compares the air condition at the outlet of the intermediate cooling section with the target air condition at the inlet of the secondary rotor to obtain the intermediate cooling deviation.

[0089] When the air temperature at the outlet of the intermediate cooling section is higher than the target temperature at the inlet of the secondary rotor, it indicates that the intermediate cooling is insufficient; when the air temperature at the outlet of the intermediate cooling section is lower than the target temperature at the inlet of the secondary rotor, it indicates that the intermediate cooling is excessive.

[0090] Furthermore, the controller determines whether the medium-temperature heat-absorbing node has sufficient cooling capacity based on the inlet temperature, outlet temperature, flow rate, and available heat exchange capacity of the heat exchange medium at the medium-temperature heat-absorbing node.

[0091] As a non-limiting example, when the inlet temperature of the heat exchange medium at the intermediate temperature heat absorber node is lower than the target inlet temperature of the secondary rotor, and the available heat exchange capacity of the intermediate temperature heat absorber node is greater than the load corresponding to the intermediate cooling deviation, the controller determines that the intermediate temperature heat absorber node can eliminate the intermediate cooling deviation.

[0092] Moreover, when the intermediate temperature heat absorption node can eliminate intermediate cooling deviation, the controller adjusts at least one of the heat exchange medium flow rate, heat absorption temperature level, and heat absorption on the high temperature stage evaporation side of the intermediate temperature heat absorption node.

[0093] For example, when intercooling is insufficient, the controller can increase the heat exchange medium flow rate at the intermediate temperature heat absorption node, decrease the heat absorption temperature of the intermediate temperature heat absorption node, or increase the heat absorption on the evaporator side of the high-temperature stage. When intercooling is excessive, the controller can decrease the heat exchange medium flow rate at the intermediate temperature heat absorption node or increase the heat absorption temperature of the intermediate temperature heat absorption node.

[0094] If the inlet temperature of the heat exchange medium at the intermediate temperature heat absorption node is not lower than the target inlet temperature of the secondary rotor, or if the available heat exchange capacity of the intermediate temperature heat absorption node reaches its upper limit but the outlet air temperature of the intermediate cooling section is still higher than the target value, the controller determines that the intermediate temperature heat absorption node cannot eliminate the intermediate cooling deviation.

[0095] Specifically, when the intermediate temperature heat absorption node cannot eliminate the intermediate cooling deviation, the controller performs at least one of the following actions: First, lower the heat absorption temperature of the intermediate-temperature heat absorption node so that the temperature of the heat exchange medium at the intermediate-temperature heat absorption node is lower than the target temperature of the intermediate cooling. Second, increase the heat exchange capacity of the intermediate-temperature heat absorption node, for example, by increasing the flow rate of the heat exchange medium at the intermediate-temperature heat absorption node, increasing the effective flow area of ​​the heat exchanger, or increasing the frequency of the relevant circulating pump. Third, call upon the low-temperature cooling node to supplement the cooling of the intermediate cooling section, for example, by opening the supplementary cooling branch valve from the low-temperature cooling node to the intermediate cooling section. Fourth, reduce the processing air load entering the intermediate cooling section, for example, by reducing the processing air flow rate, bypassing some air, or reducing the regeneration intensity of the first-stage rotor to reduce the heat adsorption and release of the first-stage rotor.

[0096] By adopting the above scheme, the high air temperature at the inlet of the secondary rotor can be avoided due to insufficient temperature level or heat exchange capacity of the intermediate heat absorption node, thereby improving the fine dehumidification capacity of the secondary rotor, stabilizing the actual supply air dew point, and enhancing the system's adaptability to fluctuations in intermediate cooling load.

[0097] Step D3: Determine the target heating state of the medium-temperature heating node based on the secondary regeneration heat load, and adjust the heating temperature, heat medium flow rate and / or low-temperature stage condensation heat distribution ratio of the medium-temperature heating node so that the secondary regeneration air flow path reaches the secondary regeneration target.

[0098] In some embodiments, the target heating state of the medium-temperature heating node is determined based on the secondary regenerative heat load.

[0099] Specifically, the medium-temperature heating node is used to provide heat to the secondary regeneration airflow path. The controller determines the target heating state of the medium-temperature heating node based on the secondary regeneration heat load.

[0100] When the secondary regenerative heat load increases, the controller can increase the outlet heat medium temperature of the medium-temperature heating node, increase the heat medium flow rate of the medium-temperature heating node, or increase the proportion of low-temperature stage condensation heat distributed to the medium-temperature heating node.

[0101] When the secondary regenerative heat load decreases, the controller can reduce the outlet heat medium temperature of the medium-temperature heating node, reduce the heat medium flow rate of the medium-temperature heating node, or reduce the proportion of low-temperature stage condensation heat allocated to the medium-temperature heating node.

[0102] In one embodiment, step D3 may specifically include: the intermediate temperature heat absorption node providing heat absorption capacity to the intermediate cooling section, including an intermediate temperature cooling correction process.

[0103] The intermediate-temperature cooling correction process includes: acquiring the air conditions at the outlet of the first-stage rotor, the air conditions at the outlet of the intermediate cooling section, the target inlet condition of the second-stage rotor, and the node conditions of the intermediate-temperature heat absorption node; determining the actual intermediate cooling load based on the air conditions at the outlet of the first-stage rotor, the air conditions at the outlet of the intermediate cooling section, and the processing air flow rate; determining the intermediate cooling deviation based on the target inlet condition of the second-stage rotor and the air conditions at the outlet of the intermediate cooling section; judging whether the intermediate-temperature heat absorption node can eliminate the intermediate cooling deviation based on the node conditions of the intermediate-temperature heat absorption node; when the intermediate-temperature heat absorption node can eliminate the intermediate cooling deviation, adjusting the heat exchange medium flow rate, heat absorption temperature, and / or the heat absorption on the evaporator side of the high-temperature stage of the intermediate-temperature heat absorption node; when the intermediate-temperature heat absorption node cannot eliminate the intermediate cooling deviation, reducing the heat absorption temperature of the intermediate-temperature heat absorption node, increasing the heat exchange capacity of the intermediate-temperature heat absorption node, calling upon the low-temperature cooling node to supplement the cooling of the intermediate cooling section, and / or reducing the processing air load entering the intermediate cooling section.

[0104] Specifically, the low-temperature stage condenser-side status may include the low-temperature stage condenser pressure, low-temperature stage condenser temperature, low-temperature stage condenser-side heat transfer fluid flow rate, or low-temperature stage condenser heat transfer. The high-temperature stage evaporator-side status may include the high-temperature stage evaporator pressure, high-temperature stage evaporator temperature, or high-temperature stage evaporator-side heat transfer. The outlet status of the intermediate-temperature heat absorption node may include the outlet heat transfer fluid temperature, outlet heat transfer fluid flow rate, or current heat supply. The target status of the secondary regenerated air may include the secondary regenerated air target temperature, target enthalpy, or target regenerated heat.

[0105] The high-temperature stage cycle obtains evaporative heat from the low-temperature stage condenser side through interstage heat exchange units. When the high-temperature stage evaporation pressure or temperature is below a preset lower limit, it indicates that the interstage heat exchange obtained by the high-temperature stage cycle is insufficient. In this case, the controller increases the proportion of low-temperature stage condensation heat allocated to the interstage heat exchange units. When the high-temperature stage evaporation pressure is within a preset range and the high-temperature stage evaporation temperature is stable, it indicates that the interstage heat exchange of the high-temperature stage cycle meets the requirements. At this time, without affecting the stable operation of the high-temperature stage cycle, some of the low-temperature stage condensation heat can be allocated to the medium-temperature heat absorption node.

[0106] When the outlet heat medium temperature of the intermediate temperature heat absorption node is lower than the heating temperature required by the target state of the secondary regenerated air, the controller determines that the intermediate temperature heat absorption node is not providing enough heat; when the actual temperature of the secondary regenerated air is lower than the target temperature of the secondary regenerated air, the controller also determines that the intermediate temperature heat absorption node is not providing enough heat.

[0107] When the heat supply from the intermediate temperature heat absorption node is insufficient, the controller can increase the proportion of low-temperature stage condensation heat allocated to the intermediate temperature heat absorption node, or increase the frequency of the low-temperature stage compressor, in order to increase the heat supply available to the intermediate temperature heat absorption node.

[0108] Furthermore, a branch line is installed on the condenser side of the low-temperature stage. The branch line includes a first branch and a second branch. The first branch connects to the interstage heat exchange unit, and the second branch connects to the intermediate-temperature heat absorption node. Electric regulating valves or three-way regulating valves can be installed on the first and second branches to achieve flow distribution.

[0109] Under the condition of meeting the interstage heat exchange requirements of the high-temperature stage cycle, the controller distributes a portion of the low-temperature stage condensation heat to the interstage heat exchange unit and another portion of the low-temperature stage condensation heat to the medium-temperature heat absorption node.

[0110] When the heating capacity of the intermediate temperature heat absorption node is lower than that of the secondary regeneration heat supply, the controller increases the proportion of low temperature stage condensation heat allocated to the intermediate temperature heat absorption node, increases the frequency of the low temperature stage compressor, or reduces the secondary regeneration air flow.

[0111] When the evaporator side of the high-temperature stage is below the preset stable operating conditions, the controller reduces the proportion of low-temperature stage condensation heat allocated to the medium-temperature heat absorption node, so that more low-temperature stage condensation heat enters the interstage heat exchange unit, thereby prioritizing the stable operation of the high-temperature stage.

[0112] Through the above steps, the heat source and regulation path of the medium-temperature heat absorption node are more clearly defined. While ensuring the stable operation of the cascade combined cooling and heating unit, the utilization rate of the low-temperature stage condensation heat is improved, the dependence of the secondary rotor regeneration on external heat sources is reduced, and the reliability of the system under variable load conditions is improved.

[0113] Step D4: Determine the target heating state of the high-temperature heating node based on the primary regeneration heat load, and adjust the heating temperature, heat medium flow rate and / or high-temperature stage compressor frequency of the high-temperature heating node so that the primary regeneration air flow path reaches the primary regeneration target; wherein, the heating temperature of the high-temperature heating node is higher than that of the medium-temperature heating node.

[0114] In some embodiments, the target heating state of the high-temperature heating node is determined based on the primary regenerative heat load.

[0115] Specifically, the high-temperature heating node is used to provide heat to the primary regeneration airflow path. The controller determines the target heating state of the high-temperature heating node based on the primary regeneration heat load.

[0116] When the primary regenerative heat load increases, the controller can raise the outlet heat medium temperature of the high-temperature heating node, increase the heat medium flow rate of the high-temperature heating node, or increase the frequency of the high-temperature stage compressor. When the primary regenerative heat load decreases, the controller can lower the outlet heat medium temperature of the high-temperature heating node, decrease the heat medium flow rate of the high-temperature heating node, or decrease the frequency of the high-temperature stage compressor.

[0117] Furthermore, the heating temperature at high-temperature heating nodes is higher than that at medium-temperature heating nodes. In this way, the first-stage rotor can obtain regenerated heat at a higher temperature, while the second-stage rotor can obtain regenerated heat at a lower temperature, thus achieving cascade utilization of regenerated heat.

[0118] By adopting the four-node matching control method in the above example, it is possible to achieve tiered matching between the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node and the pre-cooling section, the intermediate cooling section, the secondary regeneration air flow path, and the primary regeneration air flow path, respectively. This improves the efficiency of cold and heat resource utilization, reduces the consumption of high-grade heat sources, and enhances the low dew point operation stability of the two-stage rotary dehumidification system.

[0119] Step E involves driving the primary regeneration airflow path and the secondary regeneration airflow path to operate independently, and adjusting them respectively according to the primary regeneration heat load and the secondary regeneration heat load.

[0120] In some embodiments, the controller enables the primary regenerative airflow path and the secondary regenerative airflow path to be supplied with air, heated, and regulated independently, respectively. The primary regenerative airflow path is regulated according to the primary regenerative heat load, and the secondary regenerative airflow path is regulated according to the secondary regenerative heat load.

[0121] In this embodiment, the primary regeneration airflow path may include a primary regeneration fan, a primary regeneration heat exchanger, and a primary regeneration air valve. The secondary regeneration airflow path may include a secondary regeneration fan, a secondary regeneration heat exchanger, and a secondary regeneration air valve. The controller can adjust the primary regeneration fan frequency, the secondary regeneration fan frequency, the primary regeneration heat exchanger heat medium flow rate, the secondary regeneration heat exchanger heat medium flow rate, the primary impeller speed, and the secondary impeller speed, respectively.

[0122] In this way, the first-stage and second-stage impellers no longer share the same regeneration air path, but instead perform regeneration control according to their own dehumidification load, thereby improving the stability of low dew point air supply.

[0123] In some implementations, step E includes: Step E1: Determine the target temperature, target flow rate, and target rotation speed of the primary regenerated air based on the primary regeneration heat load.

[0124] In some embodiments, the primary dehumidifier rotor undertakes the main dehumidification load. The controller determines the target temperature of the primary regenerated air, the target flow rate of the primary regenerated air, and the target rotation speed of the primary regenerator rotor based on the primary regeneration heat load.

[0125] Specifically, when the dehumidification load of the first-stage rotor increases, the controller can raise the target temperature of the first-stage regenerated air, increase the target flow rate of the first-stage regenerated air, or increase the target speed of the first-stage rotor. When the dehumidification load of the first-stage rotor decreases, the controller can lower the target temperature of the first-stage regenerated air, decrease the target flow rate of the first-stage regenerated air, or decrease the target speed of the first-stage rotor.

[0126] Step E2: Determine the target temperature, target flow rate, and target rotation speed of the secondary regenerated air based on the secondary regeneration heat load.

[0127] In some embodiments, the secondary impeller undertakes the fine dehumidification load. The controller determines the target temperature of the secondary regenerated air, the target flow rate of the secondary regenerated air, and the target rotational speed of the secondary impeller based on the secondary regeneration heat load.

[0128] Specifically, when the actual supply air dew point is higher than the target supply air dew point, the controller can increase the target temperature of the secondary regenerated air, increase the target flow rate of the secondary regenerated air, or increase the target speed of the secondary impeller. When the actual supply air dew point is lower than the target supply air dew point and remains stable, the controller can decrease the target temperature of the secondary regenerated air, decrease the target flow rate of the secondary regenerated air, or decrease the target speed of the secondary impeller.

[0129] Step E3: Adjust the primary regeneration heat exchanger, primary regeneration fan, and primary regeneration wheel drive mechanism in the primary regeneration air flow path according to the primary regeneration air target temperature, primary regeneration air target flow rate, and primary regeneration wheel target speed.

[0130] In some embodiments, a primary regeneration heat exchanger, a primary regeneration fan, and a primary rotor drive mechanism are provided in the primary regeneration air flow path. The controller adjusts the heating state of the primary regeneration heat exchanger by regulating the heat transfer medium flow rate according to the target temperature of the primary regeneration air; adjusts the frequency of the primary regeneration fan or the opening degree of the primary regeneration air valve according to the target flow rate of the primary regeneration air; and adjusts the primary rotor drive mechanism according to the target rotation speed of the primary rotor.

[0131] Step E4: Adjust the secondary regeneration heat exchanger, secondary regeneration fan, and secondary rotor drive mechanism in the secondary regeneration air flow path according to the target temperature, target flow rate, and target rotation speed of the secondary regeneration air.

[0132] In some embodiments, a secondary regeneration heat exchanger, a secondary regeneration fan, and a secondary rotor drive mechanism are provided in the secondary regeneration air flow path. The controller adjusts the heat medium flow rate or heating status of the secondary regeneration heat exchanger according to the target temperature of the secondary regeneration air; adjusts the frequency of the secondary regeneration fan or the opening degree of the secondary regeneration air valve according to the target flow rate of the secondary regeneration air; and adjusts the secondary rotor drive mechanism according to the target rotation speed of the secondary rotor.

[0133] Step E5: When the dehumidification load of the first-stage rotor increases and the actual supply air dew point does not exceed the target supply air dew point, increase the target temperature of the first-stage regenerated air, the target flow rate of the first-stage regenerated air, and / or the target rotation speed of the first-stage rotor.

[0134] Step E6: When the actual supply air dew point exceeds the target supply air dew point, increase the target temperature of the secondary regenerated air, the target flow rate of the secondary regenerated air, and / or the target speed of the secondary impeller.

[0135] Step E7: When the dehumidification load of the secondary rotor is lower than the preset low load threshold, reduce the target temperature of the secondary regenerated air, reduce the target flow rate of the secondary regenerated air, reduce the target speed of the secondary rotor, and / or make the secondary regenerated air flow path operate intermittently.

[0136] In some embodiments, when the dehumidification load of the primary rotor increases but the actual supply air dew point does not exceed the target supply air dew point, it indicates that the load of the main dehumidification section of the system has increased, but the final supply air dew point has not yet gone out of control. At this time, the controller prioritizes increasing the target temperature of the primary regenerated air, the target flow rate of the primary regenerated air, or the target rotation speed of the primary rotor.

[0137] When the actual supply air dew point exceeds the target supply air dew point, it indicates that the final fine dehumidification is insufficient. In this case, the controller prioritizes increasing the target temperature of the secondary regenerated air, the target flow rate of the secondary regenerated air, or the target speed of the secondary impeller.

[0138] When the dehumidification load of the secondary rotor is lower than the preset low load threshold, the controller reduces the target temperature of the secondary regenerated air, reduces the target flow rate of the secondary regenerated air, reduces the target speed of the secondary rotor, or makes the secondary regenerated air flow path run intermittently.

[0139] In this way, the primary regenerated airflow path and the secondary regenerated airflow path are independent of each other in terms of physical airflow path and control logic, and can respectively adapt to the different needs of main dehumidification and fine dehumidification.

[0140] By adopting the above scheme, independent control of the primary dehumidifier and the secondary dehumidifier can be achieved, avoiding mutual restraint on the regeneration intensity of the two-stage rotors, improving the accuracy of supply air dew point control, and taking into account both dehumidification capacity under high load conditions and energy-saving effect under low load conditions.

[0141] Step F: Based on the target air supply dew point, the air state after the secondary rotor, and the node states of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node, the actual air supply dew point is made to approach the target air supply dew point.

[0142] In some embodiments, the actual supply air dew point can be obtained by a dew point sensor installed at the outlet of the secondary impeller or in the supply air duct, or it can be calculated based on the air temperature and relative humidity at the outlet of the secondary impeller. When the actual supply air dew point is higher than the target supply air dew point, it indicates insufficient dehumidification, and the controller can increase the secondary regeneration intensity, increase the primary regeneration intensity, enhance the intermediate cooling capacity, or enhance the pre-cooling capacity. When the actual supply air dew point is lower than the target supply air dew point and remains stable, the controller can appropriately reduce the secondary regeneration intensity, reduce the primary regeneration intensity, or reduce the cooling intensity to reduce energy consumption.

[0143] In one embodiment, step F includes: determining the actual supply air dew point based on the air condition after the secondary rotor; comparing the actual supply air dew point with the target supply air dew point to obtain the dew point deviation; generating pre-cooling correction, intermediate cooling correction, primary regeneration correction, and secondary regeneration correction based on the dew point deviation; adjusting the operating state of the low-temperature cooling node based on the pre-cooling correction and the node status of the low-temperature cooling node; adjusting the operating state of the intermediate-temperature heat absorption node based on the intermediate cooling correction and the node status of the intermediate-temperature heat absorption node; adjusting the operating state of the intermediate-temperature heating node based on the secondary regeneration correction and the node status of the intermediate-temperature heating node; adjusting the operating state of the high-temperature heating node based on the primary regeneration correction and the node status of the high-temperature heating node; and limiting, delaying, and prioritizing the adjustment amounts of the low-temperature cooling node, intermediate-temperature heat absorption node, intermediate-temperature heating node, and high-temperature heating node.

[0144] In one example, when the actual supply air dew point is slightly higher than the target supply air dew point, the controller can prioritize adjusting the medium-temperature heating node and the secondary regenerated air flow path; when the dew point deviation persists, the high-temperature heating node and the primary regenerated air flow path will be adjusted; when the inlet air temperature of the secondary rotor is higher than the target temperature, the medium-temperature heat absorption node will be prioritized or the low-temperature cooling node will be called to supplement cooling.

[0145] By adopting the above scheme, a cascade control structure can be established with the supply air dew point as the outer loop and the node states of low-temperature cooling nodes, medium-temperature heat absorption nodes, medium-temperature heating nodes, and high-temperature heating nodes as the inner loop. This improves the low dew point control accuracy, enhances the system's dynamic response capability, and improves the coordinated operation stability between the cascade combined cooling and heating unit and the two-stage rotary dehumidifier system.

[0146] In some embodiments, the control method may further include: an operating mode switching process.

[0147] The operation mode switching process includes: determining the current operation mode based on the total dehumidification load, target supply air dew point, and actual supply air dew point; when the total dehumidification load is higher than the preset high load threshold and the target supply air dew point is lower than the preset low dew point threshold, entering the high load deep dehumidification mode, in which the heating capacity of high-temperature heating nodes and medium-temperature heating nodes is increased, and the cooling capacity of low-temperature cooling nodes and / or medium-temperature heat absorption nodes is enhanced; when the total dehumidification load is lower than the preset low load threshold, entering the low load energy-saving mode, in which the regeneration of the secondary regeneration airflow path is reduced. The intensity is increased by reducing the target speed of the secondary rotor and / or intermittently operating the secondary regenerated air flow path. When the actual supply air dew point is higher than the target supply air dew point and continues for more than a preset time, the dew point recovery mode is entered. In the dew point recovery mode, the target temperature and / or target flow rate of the secondary regenerated air are increased, and the cooling capacity of the intermediate cooling section is enhanced simultaneously. When the cascade combined cooling and heating unit reaches the preset safety limit conditions, the safe load reduction mode is entered. In the safe load reduction mode, the compressor frequency of the cascade combined cooling and heating unit is reduced, the target temperature of the regenerated air is reduced, and / or the processing air load is reduced.

[0148] And the coordinated scheduling process of heat storage and auxiliary heating.

[0149] The coordinated scheduling process of heat storage and auxiliary heating includes: determining the available heat capacity of the medium-temperature heating nodes based on their node status, and determining the available heat capacity of the high-temperature heating nodes based on their node status; comparing the available heat capacity of the medium-temperature heating nodes with the secondary regenerative heat load, and comparing the available heat capacity of the high-temperature heating nodes with the primary regenerative heat load; when the available heat capacity of the medium-temperature heating nodes is greater than the secondary regenerative heat load and / or the available heat capacity of the high-temperature heating nodes is greater than the primary regenerative heat load, storing the excess heat in the heat storage unit; when the available heat capacity of the medium-temperature heating nodes is less than the secondary regenerative heat load, the heat storage unit supplements heat to the secondary regenerative airflow path, and if the secondary regenerative heat load is still not met after supplementing heat, the secondary auxiliary heating unit is activated; when the available heat capacity of the high-temperature heating nodes is less than the primary regenerative heat load, the heat storage unit supplements heat to the primary regenerative airflow path, and if the primary regenerative heat load is still not met after supplementing heat, the primary auxiliary heating unit is activated.

[0150] See Figure 3 , Figure 3 This is a comparison chart of system operating energy consumption in one embodiment of this application.

[0151] The vertical axis represents the energy consumption per unit dehumidification capacity, expressed in kWh / kg (the total electricity consumption required to remove 1 kg of moisture); the horizontal axis includes three typical operating conditions: full load in summer, partial load in the transition season, and low load in winter. Furthermore, in Figure 3In China, the traditional solution is a steam regeneration + independent refrigeration system, while this solution is a cascade unit coupled with a two-stage turbine system.

[0152] Depend on Figure 3 It can be seen that under full-load conditions in summer, the inlet air moisture content d = 18 g / kg (18 g of water vapor per kg of dry air), the target dew point DP = -40℃, the unit dehumidification energy consumption of the traditional solution is 5.0 kWh / kg, and the unit dehumidification energy consumption of the solution of this invention is 2.56 kWh / kg, which is about 49% lower than the traditional solution. This shows that under high humidity and high load conditions, the system of this invention can significantly reduce the operating energy consumption in the deep dehumidification process.

[0153] Under partial load conditions during the transitional season, with an inlet air moisture content d=12g / kg and a target dew point DP=-20℃, the energy consumption per unit of dehumidification for the traditional solution is 4.0 kWh / kg, while the energy consumption per unit of dehumidification for the solution of this invention is 2.0 kWh / kg, a reduction of approximately 50% compared to the traditional solution. This result demonstrates that under moderate humidity load conditions, the system of this invention can still maintain a high energy efficiency advantage.

[0154] Under low-load conditions in winter, with an inlet air moisture content d=8g / kg and a target dew point DP=-15℃, the energy consumption per unit of dehumidification for the traditional solution is 3.0kWh / kg, while the energy consumption per unit of dehumidification for the solution of this invention is 1.5 kWh / kg, a reduction of approximately 50% compared to the traditional solution. This demonstrates that the system of this invention also exhibits stable energy-saving effects under low-humidity and low-load operating conditions.

[0155] In summary, for different seasons and different humidity load conditions, the unit dehumidification energy consumption of the present invention is significantly lower than that of the traditional solution, with an energy saving rate of approximately 49% to 50%.

[0156] The results show that the present invention, through the coupled operation of the unit and the two-stage rotor, can effectively reduce the overall energy consumption of the regeneration and refrigeration processes while meeting the target dew point requirements, thereby improving the overall energy efficiency of the system, and is especially suitable for scenarios that require continuous and stable deep dehumidification.

[0157] This application also provides a dehumidification device.

[0158] See next Figure 2 The dehumidification device 100 may include: The cascade combined cooling and heating unit 300 includes a low-temperature stage cycle, a high-temperature stage cycle, and an interstage heat exchange unit 312 disposed between the low-temperature stage cycle and the high-temperature stage cycle.

[0159] The two-stage rotary dehumidification system 200 includes a treatment air flow path 210, a first-stage rotary wheel 214, a second-stage rotary wheel 218, a first-stage regeneration air flow path, and a second-stage regeneration air flow path. The treatment air flow path includes a pre-cooling section 213, a first-stage rotary wheel treatment area, an intermediate cooling section 216, and a second-stage rotary wheel treatment area arranged sequentially along the treatment air flow direction. The first-stage regeneration air flow path is connected to the regeneration area of ​​the first-stage rotary wheel, and the second-stage regeneration air flow path is connected to the regeneration area of ​​the second-stage rotary wheel. The first-stage regeneration air flow path and the second-stage regeneration air flow path are independent of each other. Low-temperature cooling node C1 is connected to the pre-cooling section 213 for heat exchange; medium-temperature heat absorption node C2 is connected to the intermediate cooling section 216 for heat exchange; medium-temperature heating node H1 is connected to the secondary regenerated air flow path 223 for heat exchange; and high-temperature heating node H2 is connected to the primary regenerated air flow path 224 for heat exchange.

[0160] The controller 400 is connected to the cascade combined cooling and heating unit 300, the primary regenerated air flow path, the secondary regenerated air flow path, the primary impeller 214 and the secondary impeller 218, and is configured to execute the control method of any of the foregoing embodiments.

[0161] In this embodiment, the primary rotor 214 includes: a first region 214a located at the top, and a second region 214b isolated from the first region 214a and connected to the primary regenerated air flow path 224.

[0162] The secondary rotor 218 includes: a third region 218a located at the top, and a fourth region 218b isolated from the third region 218a and connected to the secondary regenerated air flow path 223.

[0163] In addition, a first regulating valve TV1 and a first temperature sensor TE_C1 are installed in the passage from the precooling section 213 to the low-temperature cooling node C1; a second regulating valve TV2 and a second temperature sensor TE_C2 are installed in the passage from the intermediate cooling section 216 to the medium-temperature heat absorption node C2; ​​a fourth regulating valve TV4, a fourth temperature sensor TE_H2 and a flow sensor FE are installed in the passage from the primary regenerated air flow path 224 to the high-temperature heating node H2; and a third regulating valve TV3 and a third temperature sensor TE_H1 are installed in the passage from the secondary regenerated air flow path 223 to the medium-temperature heating node H1.

[0164] In some embodiments, a third fan 222 is provided at the regeneration air outlet of the primary rotor 214. The exhaust end of the third fan 222 is connected to the dehumidification outlet. Furthermore, the cascade combined cooling and heating unit may also include: a high-temperature stage compressor 311, and a high-temperature stage condenser 315 connected to the high-temperature stage compressor 311, with both the high-temperature stage compressor 311 and the high-temperature stage condenser 315 connected to the interstage heat exchange unit 312. For example, the high-temperature stage condenser 315 is connected to the interstage heat exchange unit 312 via a high-temperature stage throttling valve 317.

[0165] The system includes a cryogenic stage compressor 313 and a cryogenic stage condenser 314 connected to the cryogenic stage compressor 313, both of which are connected to an interstage heat exchange unit 312. For example, the cryogenic stage condenser 314 is connected to the interstage heat exchange unit 312 via a cryogenic stage throttle valve 316.

[0166] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0167] The above embodiments merely illustrate several implementation methods of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A control method for a dehumidification device, characterized in that, The dehumidification device includes: a cascade combined cooling and heating unit and a two-stage rotary dehumidification system. The two-stage rotary dehumidification system includes a processing air flow path, a first-stage rotary wheel, a second-stage rotary wheel, a first-stage regeneration air flow path, and a second-stage regeneration air flow path. The processing air flow path includes a pre-cooling section, a first-stage rotary wheel processing area, an intermediate cooling section, and a second-stage rotary wheel processing area arranged sequentially along the processing air flow direction. The cascade combined cooling and heating unit forms a low-temperature cooling node, a medium-temperature heat absorption node, a medium-temperature heating node, and a high-temperature heating node. The control method includes: Step A: Obtain the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air status before and after the first-stage impeller, the air status before and after the second-stage impeller, the air status of the first-stage regenerated air, the air status of the second-stage regenerated air, and the node status of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node. Step B: Determine the pre-cooling load, intermediate cooling load, first-stage dehumidification load, and second-stage dehumidification load of the processed air based on the inlet temperature and humidity of the processed air, the target supply air dew point, the processed air flow rate, the air conditions before and after the first-stage impeller, and the air conditions before and after the second-stage impeller. Step C: Determine the primary regeneration heat load based on the primary dehumidification load and the primary regeneration air state, and determine the secondary regeneration heat load based on the secondary dehumidification load and the secondary regeneration air state; Step D involves controlling the low-temperature cooling node to provide cooling capacity to the pre-cooling section, controlling the medium-temperature heat absorption node to provide heat absorption capacity to the intermediate cooling section, controlling the medium-temperature heating node to provide heat to the secondary regeneration air flow path, and controlling the high-temperature heating node to provide heat to the primary regeneration air flow path. This includes: determining the target cooling state of the low-temperature cooling node based on the pre-cooling load of the processed air, and adjusting the evaporation temperature, refrigerant flow rate, and / or low-temperature compressor frequency of the low-temperature cooling node to ensure that the outlet air state of the pre-cooling section reaches the pre-cooling target; determining the target heat absorption state of the medium-temperature heat absorption node based on the intermediate cooling load, and adjusting the heat absorption temperature and heat exchange medium of the medium-temperature heat absorption node. The flow rate and / or the heat absorbed by the high-temperature stage evaporator are adjusted to ensure that the outlet air condition of the intermediate cooling section reaches the intermediate cooling target. The target heating state of the medium-temperature heating node is determined based on the secondary regeneration heat load, and the heating temperature, heat medium flow rate, and / or the low-temperature stage condensation heat distribution ratio of the medium-temperature heating node are adjusted to ensure that the secondary regeneration airflow path reaches the secondary regeneration target. The target heating state of the high-temperature heating node is determined based on the primary regeneration heat load, and the heating temperature, heat medium flow rate, and / or the high-temperature stage compressor frequency of the high-temperature heating node are adjusted to ensure that the primary regeneration airflow path reaches the primary regeneration target. The heating temperature of the high-temperature heating node is higher than that of the medium-temperature heating node. Step E involves driving the primary regeneration airflow path and the secondary regeneration airflow path to operate independently, and adjusting them respectively according to the primary regeneration heat load and the secondary regeneration heat load; Step F: Based on the target air supply dew point, the air state after the secondary rotor, and the node states of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node, and the high-temperature heating node, the actual air supply dew point is made to approach the target air supply dew point.

2. The control method according to claim 1, characterized in that, The processed air inlet temperature and humidity include the processed air inlet temperature and the processed air inlet relative humidity; Step B includes: The moisture content of the processed air inlet is calculated based on the processed air inlet temperature and the processed air inlet relative humidity. Calculate the target supply air moisture content based on the target supply air dew point; The total dehumidification load is calculated based on the moisture content of the treated air inlet, the target moisture content of the supply air, and the treated air flow rate. According to the principle that the first-stage dehumidifier bears the main dehumidification load and the second-stage dehumidifier bears the fine dehumidification load, the total dehumidification load is allocated to the initial value of the dehumidification load of the first-stage dehumidifier and the initial value of the dehumidification load of the second-stage dehumidifier; The difference in air humidity before and after the first-stage impeller is calculated based on the air state before and after the first-stage impeller, and the initial value of the dehumidification load of the first-stage impeller is corrected based on the difference in air humidity before and after the first-stage impeller to obtain the dehumidification load of the first-stage impeller; The difference in air humidity before and after the secondary impeller is calculated based on the air state before and after the secondary impeller, and the initial value of the dehumidification load of the secondary impeller is corrected based on the difference in air humidity before and after the secondary impeller to obtain the dehumidification load of the secondary impeller; The precooling load of the processed air is determined based on the inlet temperature of the processed air, the target precooling temperature, and the flow rate of the processed air. The intermediate cooling load is determined based on the air temperature at the outlet of the first-stage rotor, the target temperature at the inlet of the second-stage rotor, and the processing air flow rate.

3. The control method according to claim 1, characterized in that, The provision of heat from the medium-temperature heating node to the secondary regenerated airflow path includes a low-temperature stage condensation heat diversion control process, which comprises: Acquire the status of the low-temperature stage condenser side, the high-temperature stage evaporator side, the outlet status of the medium-temperature heating node, and the target status of the secondary regenerated air; The required interstage heat exchange for the high-temperature stage cycle is determined based on the evaporator side condition of the high-temperature stage. The required secondary regenerated heat supply for the medium-temperature heating node is determined based on the outlet status of the medium-temperature heating node and the target status of the secondary regenerated air. Under the condition of meeting the interstage heat exchange requirements of the high-temperature stage cycle, a portion of the low-temperature stage condensation heat is allocated to the interstage heat exchange unit, and another portion of the low-temperature stage condensation heat is allocated to the medium-temperature heating node. When the heating capacity of the medium-temperature heating node is lower than that of the secondary regeneration heating capacity, the proportion of the low-temperature stage condensation heat allocated to the medium-temperature heating node is increased, the frequency of the low-temperature stage compressor is increased, and / or the secondary regeneration air flow rate is reduced. When the evaporation side of the high-temperature stage is below the preset stable operating conditions, the proportion of the condensation heat of the low-temperature stage distributed to the medium-temperature heating node is reduced to ensure the stable operation of the high-temperature stage.

4. The control method according to claim 1, characterized in that, The provision of heat absorption capacity from the intermediate temperature heat absorption node to the intermediate cooling section includes an intermediate temperature cooling correction process, which includes: Acquire the air status at the outlet of the first-stage rotor, the air status at the outlet of the intermediate cooling section, the target status at the inlet of the second-stage rotor, and the node status of the intermediate-temperature heat absorption node; The actual load of the intermediate cooling system is determined based on the air condition at the outlet of the first-stage rotor, the air condition at the outlet of the intermediate cooling section, and the processing air flow rate. The intermediate cooling deviation is determined based on the target state at the inlet of the secondary rotor and the air state at the outlet of the intermediate cooling section. Determine whether the intermediate cooling deviation can be eliminated based on the node status of the intermediate temperature heat absorption node; When the intermediate temperature heat absorption node can eliminate the intermediate cooling deviation, adjust the heat exchange medium flow rate, heat absorption temperature level and / or the heat absorption of the high temperature stage evaporation side of the intermediate temperature heat absorption node. When the intermediate temperature heat absorption node cannot eliminate the intermediate cooling deviation, the heat absorption temperature of the intermediate temperature heat absorption node is reduced, the heat exchange capacity of the intermediate temperature heat absorption node is increased, the low temperature cooling node is called to supplement the cooling of the intermediate cooling section, and / or the processing air load entering the intermediate cooling section is reduced.

5. The control method according to claim 1, characterized in that, Step E includes: The target temperature, target flow rate, and target rotation speed of the primary regenerator are determined based on the primary regenerator heat load. The target temperature, target flow rate, and target rotation speed of the secondary regenerator are determined based on the secondary regenerator heat load. Based on the target temperature of the primary regenerated air, the target flow rate of the primary regenerated air, and the target rotation speed of the primary rotor, adjust the primary regenerated heat exchanger, the primary regenerated fan, and the primary rotor drive mechanism in the primary regenerated air flow path; Based on the target temperature of the secondary regenerated air, the target flow rate of the secondary regenerated air, and the target rotation speed of the secondary rotor, adjust the secondary regenerated heat exchanger, the secondary regenerated fan, and the secondary rotor drive mechanism in the secondary regenerated air flow path; When the dehumidification load of the first-stage rotor increases and the actual supply air dew point does not exceed the target supply air dew point, the target temperature of the first-stage regenerated air, the target flow rate of the first-stage regenerated air, and / or the target rotation speed of the first-stage rotor are increased. When the actual supply air dew point exceeds the target supply air dew point, increase the target temperature of the secondary regenerated air, the target flow rate of the secondary regenerated air, and / or the target rotation speed of the secondary impeller. When the dehumidification load of the secondary rotor is lower than the preset low load threshold, the target temperature of the secondary regenerated air is reduced, the target flow rate of the secondary regenerated air is reduced, the target rotation speed of the secondary rotor is reduced, and / or the secondary regenerated air flow path is made to operate intermittently.

6. The control method according to claim 1, characterized in that, Step F includes: The actual supply air dew point is determined based on the air condition after the secondary rotor. The actual supply air dew point is compared with the target supply air dew point to obtain the dew point deviation; Based on the dew point deviation, pre-cooling correction, intermediate cooling correction, first-stage regeneration correction, and second-stage regeneration correction are generated; The operating status of the low-temperature cooling node is adjusted according to the precooling correction amount and the node status of the low-temperature cooling node. The operating state of the intermediate temperature heat absorption node is adjusted according to the intermediate cooling correction amount and the node status of the intermediate temperature heat absorption node; The operating status of the medium-temperature heating node is adjusted according to the secondary regeneration correction amount and the node status of the medium-temperature heating node. The operating status of the high-temperature heating node is adjusted according to the first-level regeneration correction amount and the node status of the high-temperature heating node; and the adjustment amounts of the low-temperature cooling node, the medium-temperature heat absorption node, the medium-temperature heating node and the high-temperature heating node are limited, delayed and sorted.

7. The control method according to claim 2, characterized in that, Also includes: The operation mode switching process includes: The current operating mode is determined based on the total dehumidification load, the target supply air dew point, and the actual supply air dew point. When the total dehumidification load is higher than the preset high load threshold and the target supply air dew point is lower than the preset low dew point threshold, the high load deep dehumidification mode is entered. In the high load deep dehumidification mode, the heating capacity of the high temperature heating node is improved, the heating capacity of the medium temperature heating node is improved, and the cooling capacity of the low temperature cooling node and / or the medium temperature heat absorption node is enhanced. When the total dehumidification load is lower than the preset low load threshold, the system enters the low load energy-saving mode. In the low load energy-saving mode, the regeneration intensity of the secondary regeneration air flow path is reduced, the target speed of the secondary impeller is reduced, and / or the secondary regeneration air flow path is made to operate intermittently. When the actual supply air dew point is higher than the target supply air dew point and continues for more than a preset time, the dew point recovery mode is entered. In the dew point recovery mode, the target temperature of the secondary regenerated air and / or the target flow rate of the secondary regenerated air are increased, and the cooling capacity of the intermediate cooling section is enhanced simultaneously. When the cascade combined cooling and heating unit reaches the preset safety limit, it enters the safety load reduction mode. In the safety load reduction mode, the compressor frequency of the cascade combined cooling and heating unit is reduced, the target temperature of the regenerated air is reduced, and / or the processing air load is reduced.

8. The control method according to claim 1, characterized in that, It also includes a coordinated scheduling process for thermal storage and auxiliary heating, which includes: The available heat capacity of the medium-temperature heating node is determined based on the node status of the medium-temperature heating node, and the available heat capacity of the high-temperature heating node is determined based on the node status of the high-temperature heating node. The available heat capacity of the medium-temperature heating node is compared with the secondary regenerative heat load, and the available heat capacity of the high-temperature heating node is compared with the primary regenerative heat load. When the heat supply capacity of the medium-temperature heating node is greater than the secondary regenerative heat load and / or the heat supply capacity of the high-temperature heating node is greater than the primary regenerative heat load, the excess heat will be stored in the heat storage unit. When the heat supply of the medium-temperature heating node is less than the secondary regeneration heat load, the heat storage unit supplements the heat to the secondary regeneration air flow path, and if the heat supplementation still cannot meet the secondary regeneration heat load, the secondary auxiliary heating unit is activated. When the heat supply of the high-temperature heating node is less than the primary regenerative heat load, the heat storage unit supplements the heat to the primary regenerative airflow path, and if the heat supplementation still cannot meet the primary regenerative heat load, the primary auxiliary heating unit is activated.

9. A dehumidification device, characterized in that, include: A cascade combined cooling and heating unit includes a low-temperature stage cycle, a high-temperature stage cycle, and an interstage heat exchange unit disposed between the low-temperature stage cycle and the high-temperature stage cycle; A two-stage rotary dehumidification system includes a treatment airflow path, a primary rotary wheel, a secondary rotary wheel, a primary regeneration airflow path, and a secondary regeneration airflow path. The treatment airflow path includes a precooling section, a primary rotary wheel treatment area, an intermediate cooling section, and a secondary rotary wheel treatment area arranged sequentially along the treatment airflow direction. The primary regeneration airflow path is connected to the regeneration area of ​​the primary rotary wheel, and the secondary regeneration airflow path is connected to the regeneration area of ​​the secondary rotary wheel. The primary regeneration airflow path and the secondary regeneration airflow path are independent of each other. The low-temperature cooling node is connected to the pre-cooling section for heat exchange; the medium-temperature heat absorption node is connected to the intermediate cooling section for heat exchange; the medium-temperature heating node is connected to the secondary regenerated air flow path for heat exchange; and the high-temperature heating node is connected to the primary regenerated air flow path for heat exchange. The controller is connected to the cascade combined cooling and heating unit, the primary regenerative airflow path, the secondary regenerative airflow path, the primary impeller, and the secondary impeller, and is configured to perform the control method according to any one of claims 1 to 8.

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