Comprehensive control method for mixed operation of roof radiant cooling and independent fresh air dehumidification system

Abstract

The invention discloses a roof radiant cooling and independent fresh air dehumidification system mixed operation comprehensive control method, and belongs to the technical field of building environment control and heating ventilation air conditioning. The method comprises the steps that the radiant cooling capacity and the dehumidification capacity of a surface air cooler are calculated through a heat balance equation, and an optimization objective that a top plate radiation system bears 70% sensible heat load and a fresh air system bears 90% humidity load is set; an anti-condensation strategy is triggered by combining dew point temperature monitoring, a control variable is adjusted by taking minimization of energy consumption as a target in a rolling time domain, and it is ensured that the indoor temperature ranges from 23 DEG C to 26 DEG C, the humidity ranges from 40% to 60%, the black ball temperature difference is smaller than or equal to 2 DEG C, and the condensation risk is smaller than or equal to 6%. The method is suitable for energy-saving temperature and humidity regulation and control of large public buildings, and efficient cooperative processing of sensible heat and latent heat loads is achieved.

Description

Technical Field

[0001] The present invention belongs to the technical field of building environment control and HVAC, and more specifically, to a comprehensive control method for mixed operation of a ceiling radiation cooling system and an independent fresh air dehumidification system. Background Art

[0002] In the field of building environmental control, the combined application of ceiling radiation cooling system and independent fresh air dehumidification system has been regarded as a temperature and humidity control method with great energy-saving potential. However, the coordinated operation of the two types of systems in the existing technology still has significant defects, mainly reflected in the imbalance of heat and humidity load distribution, insufficient adaptability to dynamic working conditions, and difficulty in balancing system energy consumption and comfort. Due to the differences in heat and mass transfer characteristics between the two types of systems, traditional control methods usually adopt fixed load distribution ratios or control strategies based on static models, which cannot effectively adapt to the dynamic fluctuations of sensible heat and humidity loads inside the building. For example, when the indoor population density or equipment heat generation suddenly changes, the ceiling radiation system may be forced to increase the cooling capacity due to the hysteresis of the sensible heat load response, resulting in its surface temperature being too low, while the fresh air system fails to compensate for the change in humidity load in time, causing the indoor relative humidity to exceed the set range. This static distribution mode not only increases the risk of condensation (especially under high humidity conditions in transitional seasons), but also significantly increases energy consumption due to frequent start-stop or overshoot operation of the two systems. In the past, attempts have been made to improve system adaptability by increasing sensor density or introducing fuzzy logic control, but the former significantly increases hardware costs and is susceptible to measurement noise, while the latter results in excessive real-time computing load due to the expansion of the rule base. In addition, the coupled transfer characteristics of sensible heat and wet loads (such as fresh air cooling that simultaneously generates sensible heat and latent heat exchange) further increase the difficulty of decoupling control variables, making it difficult for traditional PID or rule control to meet the needs of refined regulation. These technical bottlenecks have long restricted the promotion and application of hybrid systems in buildings in complex climate zones. Summary of the invention

[0003] An object of the present invention is to provide a comprehensive control method for mixed operation of ceiling radiation cooling and independent fresh air dehumidification system to solve the following technical problems:

[0004] The traditional ceiling radiation and fresh air dehumidification hybrid system has high energy consumption, high condensation risk and insufficient comfort due to the imbalance of heat and humidity load distribution. The existing method lacks a mechanism to dynamically separate sensible heat and humidity loads, and cannot adjust water supply and air supply parameters according to real-time working conditions, resulting in delayed or overshooting of system response.

[0005] The existing anti-condensation control adopts a fixed threshold alarm, which cannot quantify the dynamic coupling relationship between the condensation probability and the comfort index, resulting in frequent fluctuations in indoor temperature and humidity or conservative strategies.

[0006] The modeling of the radiation cooling system ignores the heat transfer loss in the pipeline, the non-uniform heat transfer effect and the influence of the heat pump linkage. The error of the steady-state model causes the cooling capacity prediction deviation to exceed 15%, affecting the load distribution accuracy.

[0007] The fresh air dehumidification model does not take into account the efficiency attenuation of the surface cooler and the dynamic control of condensation. The dehumidification capacity calculation deviates from the actual working conditions and the wet load sharing ratio is inaccurate.

[0008] The separation of sensible heat and wet loads lacks dynamic constraint equations, and the static allocation rules cannot adapt to load fluctuations, resulting in the load sharing ratio of the ceiling radiation and fresh air system deviating from the preset target (70% sensible heat, 90% wet load).

[0009] The existing MPC strategy does not combine anti-condensation constraints and load distribution priorities. The single optimization target leads to a local optimal solution, which makes it difficult to achieve the lowest global energy consumption and controllable risks.

[0010] After the anti-condensation strategy is triggered, the wall temperature safety margin is not prioritized. Directly adjusting the parameters may cause secondary temperature and humidity imbalance, exacerbating system instability.

[0011] The weight of the load distribution penalty item is fixed and cannot adapt to the dynamic changes of outdoor climate (such as alternation of high temperature and high humidity), resulting in a decrease in the adaptability of the control strategy.

[0012] The water supply and air supply temperature adjustment range does not define the temporary operating condition tolerance. When the anti-condensation strategy is implemented, the sudden change in temperature may cause equipment failure or deterioration of comfort. The cold source connection method does not distinguish between high and low temperature cold source characteristics, resulting in reduced energy efficiency of the heat pump system or insufficient dehumidification capacity.

[0013] In order to achieve these purposes and other advantages of the present invention, according to one aspect of the present invention, the present invention provides a method for controlling the mixed operation of a ceiling radiation cooling system and an independent fresh air dehumidification system, comprising the following steps:

[0014] Real-time collection of building system parameters and indoor environmental parameters, including supply and return water temperature of the ceiling radiation cooling system, inlet and outlet water temperature of the independent fresh air dehumidification system, and supply and return water temperature of the evaporator side of the heat pump system; indoor environmental parameters including ceiling wall temperature, indoor air humidity and black globe temperature;

[0015] Based on the real-time data collected, model the ceiling radiation cooling system and the independent fresh air dehumidification system;

[0016] Based on the heat and moisture load coordinated distribution rule, the separation and optimization of sensible heat and moisture loads are achieved through dynamic constraints, so that the sensible heat load is dominated by the ceiling radiation cooling system, and the moisture load is dominated by the independent fresh air dehumidification system;

[0017] Based on the radiation cooling system model and the fresh air dehumidification system model, as well as the sensible heat load and wet load dominant strategy, the model predictive control MPC strategy is adopted to minimize energy consumption while meeting the indoor comfort and condensation risk standards, and adjust the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system in real time;

[0018] Among them, the dominant strategies for sensible heat load and wet load are: the ceiling radiation cooling system bears a proportion of sensible heat load ≥ 70%; the independent fresh air dehumidification system bears a proportion of wet load ≥ 90%.

[0019] Preferably, in the integrated control method for mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system, the condensation risk level reaches the standard of condensation risk threshold probability ≤ 4-6%;

[0020] Indoor comfort standards include: indoor air temperature: 23–26°C in summer, 20–24°C in winter; indoor air humidity: 40%–60% RH; the difference between the black globe temperature and the air temperature ≤ 2°C.

[0021] Preferably, in the integrated control method for the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system, the modeling of the ceiling radiation cooling system includes:

[0022] Dynamic calculation of cooling capacity: based on real-time acquisition of the water supply temperature T of the ceiling radiation cooling system supply , unit ℃, return water temperature T return , unit ℃; circulating water flow m water , unit kg / s; and water specific heat capacity at constant pressure C p Unit: kJ / (kg·K), calculate the real-time cooling capacity Q through the heat balance equation rad :

[0023] Q rad =a 10 ·m water ·c p ·(T return -T supply )

[0024] Among them, a 10 is the correction factor for the radiation system, which is between 0.9 and 1.1 and is used to calibrate the heat transfer loss in the pipeline and the non-uniform heat transfer effect at the end;

[0025] Top plate radiation surface heat transfer model: Combine the top plate wall temperature Twall, unit: ℃ and the black ball temperature T black , unit: ℃ Establish the equivalent heat transfer model between the radiation surface and the indoor environment:

[0026] Q rad，eff =U eq ·A·(Twall -T black )

[0027] Where U eq =k1·(T black -T air )+k2, is the dynamic equivalent heat transfer coefficient, unit: W / (m 2 ·K); k1, and k2 are determined by fitting experimental data, A is the radiation surface area, unit: m 2 , Q rad，eff is the actual effective cooling capacity;

[0028] Linkage with the heat pump system: water supply temperature T on the evaporator side of the heat pump system evap,supply , unit: ℃ and return water temperature T evap,return , unit: ℃, real-time calculation of heat pump cooling capacity Q HP , unit: kW:

[0029] Q HP =m HP ·c p ·(T evap，return -T evap.supply )

[0030] Among them, m HP Represents the heat pump circulating water flow rate, unit: kg / s; parameter Q HP Used to calibrate the consistency between the cooling capacity of the radiation system and the output of the heat pump to avoid system overshoot;

[0031] Among them, Q rad，eff ≤Q rad , and if Q rad，eff >Q HP , indicating that the heat pump is insufficient, then reduce the water supply temperature of the radiation system or increase the water flow; if Q rad，eff <Q HP , indicating that the heat pump is over-supplied, so the water supply temperature should be increased or the water flow rate should be reduced.

[0032] Preferably, in the integrated control method for the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system, the modeling of the independent fresh air dehumidification system includes:

[0033] Dynamic dehumidification capacity calculation: based on the water inlet temperature T of the independent fresh air dehumidification system cool，in Unit: ℃, water outlet temperature T cool，out Unit: ℃; air volume m air , unit kg / s, and indoor air humidity d in , unit: g / kg, outdoor air humidity d out , unit g / kg, construct dehumidification model:

[0034] Wdehum =a 20 ·m air ·(d in -d out )

[0035] Among them, a 20 W is the surface cooler efficiency correction factor, which is between 1.0 and 1.05 and is used to compensate for the effects of frost or dirt on the heat exchanger surface. dehum is the dehumidification capacity, unit: g / s, which means the mass of water removed per unit time;

[0036] Sensible cooling capacity calculation:

[0037] Q fan =m air ·c p，air ·(T in -T out )

[0038] In the formula, c p，air is the specific heat capacity of air, which is 1.005 kU / (kg·K), T in T out are the air temperatures before and after treatment, in ℃, Q fan The sensible cooling capacity, unit: W, represents the sensible cooling capacity provided by the fresh air system through cooling;

[0039] Dynamic control of condensation risk: real-time monitoring of air dew point temperature T dew and top wall temperature T wall , when T wall -T dew When the temperature is ≤1℃, the anti-condensation strategy is triggered: the outlet water temperature of the surface cooler is increased by 2-3℃, and the fresh air supply volume is reduced by 10%-15%.

[0040] Preferably, in the integrated control method for the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system, the separation optimization of the sensible heat and the wet load is achieved by the following equation:

[0041]

[0042] Among them, Q total is the total sensible heat load, representing the total sensible heat cooling load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; Q rad is the real-time cooling capacity of the ceiling radiation cooling system; Q fan Q is the sensible heat cooling capacity of the independent fresh air dehumidification system; design is the design sensible heat load, which represents the theoretical maximum sensible heat cooling load under the system design condition; and

[0043] W totalis the total wet load, representing the total wet load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; W dehum is the dehumidification capacity of the independent fresh air dehumidification system; W infiltration W is the infiltration moisture load, which represents the moisture that penetrates from the outside due to insufficient air tightness of the building; design is the design wet load, which represents the theoretical maximum wet load under the system design conditions.

[0044] Preferably, in the integrated control method for the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system, real-time adjustment of the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the independent fresh air dehumidification system comprises the following steps:

[0045] The MPC optimization objective function is defined as minimizing the total energy consumption of the system:

[0046] min(W HP +W pump +W fan )

[0047] Among them, the heat pump energy consumption W HP , water pump energy consumption W pump , fan energy consumption W fan Respectively with the heat pump cooling capacity Q HP , circulating water flow m water , air supply volume m air Positive correlation;

[0048] Solve the optimization problem in the rolling time domain and dynamically adjust the control variables:

[0049] When the sensible heat load ratio is less than 70%, reduce the water supply temperature T of the top plate radiation system. supply , improve the actual effective cooling capacity Q rad,eff ;

[0050] When the wet load ratio is less than 90%, reduce the fresh air supply temperature T fan , improve the dehumidification capacity of the independent fresh air dehumidification system W dehum ;

[0051] When T is detected wall -T dew ≤1℃, trigger the anti-condensation strategy: increase T supply 1–2℃, reduce radiant cooling; increase T fan 2–3°C, reduce dehumidification priority;

[0052] Output optimized water supply temperature T supply and supply air temperature T fan , real-time regulation of ceiling radiation cooling and independent fresh air dehumidification system operation.

[0053] Preferably, in the integrated control method for the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system, in the step of solving the optimization problem in the rolling time domain and dynamically adjusting the control variables: after the anti-condensation strategy is triggered, priority is given to ensuring T wall ≥T dew +1 degree Celsius, and then redistribute the heat and moisture load through MPC.

[0054] Preferably, in the above-mentioned integrated control method for mixed operation of ceiling radiation cooling and independent fresh air dehumidification system,

[0055] Introducing the penalty term λ1·max(0.70%-R sen，rad ), and λ2·max(0,90%-R hum，fan ), enforcing load distribution constraints;

[0056] The weight coefficients λ1 and λ2 are dynamically adjusted according to the outdoor temperature and humidity: λ2 increases in high humidity weather, and λ1 increases in high temperature weather;

[0057] Among them, R sen,rad : The proportion of sensible heat load borne by the ceiling radiation system; R hum,fan : The wet load ratio of the independent fresh air dehumidification system, the value range is: 0.5≤λ1≤3.0, 0.5≤λ2≤3.0.

[0058] Preferably, in the integrated control method for the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system, the water supply temperature adjustment range is 18-22°C, and the supply air temperature adjustment range is 12-16°C; when the anti-condensation strategy is executed, the supply air temperature is allowed to temporarily exceed the lower limit to 10°C, but the duration is ≤5 minutes.

[0059] Preferably, the integrated control method for mixed operation of ceiling radiation cooling and independent fresh air dehumidification system further includes: a high-temperature cold source is directly connected to the ceiling radiation cooling system, and a low-temperature cold source is connected to the independent fresh air dehumidification system.

[0060] The present invention has achieved at least the following beneficial effects:

[0061] The comprehensive control method of the present invention significantly improves the operating efficiency and reliability of the hybrid system through dynamic modeling and collaborative optimization. The radiation cooling system model constructed based on real-time data introduces the dynamic equivalent heat transfer coefficient, reduces the cooling capacity prediction error from 15% to less than 5%, and combines the heat pump linkage calibration mechanism to reduce the energy consumption waste caused by energy supply imbalance by 8-10%; the fresh air dehumidification model adopts the surface cooler efficiency correction coefficient to improve the dehumidification calculation accuracy by 20%, and the wet load sharing deviation is controlled below 3%. Through the design of sensible heat and wet load separation equations and exponential decay factors, the system can still compress the deviation ratio of 70% of the sensible heat load borne by the top plate and 90% of the wet load borne by the fresh air from ±15% to ±5% under load mutation conditions. The model predictive control strategy is combined with the dynamic penalty item weight adjustment to achieve a global energy consumption reduction of 12-18%, while the condensation risk incidence rate is reduced to less than 4%, and the system stability is improved by 30% by giving priority to ensuring the wall temperature safety boundary. The tolerance design for the temporary break of the lower limit of the air supply temperature reduces the equipment failure rate under emergency anti-condensation conditions by 50%, and the differentiated connection of high and low temperature cold sources increases the energy efficiency ratio of the heat pump by 0.3-0.5. Finally, the system maintains an indoor temperature of 23-26℃, humidity of 40%-60%, and a black ball temperature difference of ≤2℃, with a comfort compliance rate of more than 95%, and the condensation warning response time is shortened to within 30 seconds.

[0062] Other advantages, objectives and features of the embodiments of the present invention will be reflected in part through the following description, and in part will be understood by those skilled in the art through study and practice of the embodiments of the present invention. DETAILED DESCRIPTION

[0063] The present invention is further described in detail below in conjunction with embodiments so that those skilled in the art can implement the invention with reference to the description.

[0064] The present invention provides a method for controlling the mixed operation of a ceiling radiation cooling system and an independent fresh air dehumidification system, comprising the following steps:

[0065] Real-time collection of building system parameters and indoor environmental parameters, the system parameters include the supply and return water temperature of the ceiling radiation cooling system, the inlet and outlet water temperature of the independent fresh air dehumidification system, and the supply and return water temperature of the evaporator side of the heat pump system. The indoor environmental parameters include the ceiling wall temperature, indoor air humidity and black globe temperature; refers to the operating status parameters of the ceiling radiation cooling system, independent fresh air dehumidification system and heat pump system, including supply and return water temperature, flow rate, etc. Indoor environmental parameters refer to indoor physical quantities directly measured by sensors, such as wall temperature, air humidity, black globe temperature, etc.

[0066] Based on the real-time data collected, model the ceiling radiation cooling system and the independent fresh air dehumidification system;

[0067] Based on the law of coordinated distribution of heat and moisture loads, the separation and optimization of sensible heat and moisture loads are achieved through dynamic constraints, so that the sensible heat load is dominated by the ceiling radiation cooling system, and the moisture load is dominated by the independent fresh air dehumidification system; the law of coordinated distribution of heat and moisture loads is based on the load distribution strategy with dynamic constraints, and the separation control of sensible heat and moisture loads is achieved through mathematical optimization.

[0068] Based on the radiation cooling system model and the fresh air dehumidification system model, as well as the sensible heat load and wet load dominant strategy, the model predictive control MPC strategy is adopted to minimize energy consumption while meeting the indoor comfort and condensation risk standards, and adjust the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system in real time;

[0069] The dominant strategy for sensible heat load and wet load is: the ceiling radiation cooling system bears ≥70% of the sensible heat load; the independent fresh air dehumidification system bears ≥90% of the wet load. As a preference, the independent fresh air dehumidification system bears more than 100% of the wet load and bears the remaining (within 30%) of the sensible heat load.

[0070] Sensible heat load: the heat transferred by the change of air temperature, unit kW. Wet load: the latent heat released by the condensation of water vapor in the air, unit g / s. Condensation risk: the probability value of the wall temperature being lower than the air dew point temperature.

[0071] A distributed sensor network is used and arranged in various areas of the building: PT100 temperature sensor (accuracy ±0.1℃) monitors the supply and return water temperature; ultrasonic flow meter (accuracy ±1.5%) measures the water flow; capacitive humidity sensor (accuracy ±3%RH) detects air humidity; black ball thermometer (accuracy ±0.5℃) obtains comprehensive thermal environment parameters

[0072] Roof radiation system: Establish a three-dimensional unsteady-state heat transfer model, taking into account the heat storage characteristics of concrete and the density of pipeline layout;

[0073] Fresh air system: A dynamic dehumidification model is established based on the surface cooler efficiency curve, including a frost compensation algorithm;

[0074] Heat pump system: Use the pressure-enthalpy diagram method to build a refrigeration cycle model, and calibrate parameters based on actual operating data;

[0075] Sensible heat distribution: When the radiation system takes less than 70% of the load, start the heat pump variable frequency regulation; Wet load distribution: Dynamic adjustment of dehumidification capacity is achieved by controlling the water temperature of the surface cooler; Collaborative optimization: Establish a heat and humidity load matrix and use the Lagrange multiplier method to solve the optimal solution. Using the method of the present invention, the system energy efficiency ratio is improved by more than 30%. The indoor temperature and humidity fluctuations are controlled within the range of ±0.5℃ / ±5% RH, and the condensation risk probability is stabilized below the 4-6% threshold.

[0076] In the above scheme, as a preferred embodiment, the condensation risk level is ≤4-6% of the condensation risk threshold probability;

[0077] Indoor comfort standards include: indoor air temperature: 23-26℃ in summer, 20-24℃ in winter; indoor air humidity: 40%-60% RH; the difference between the black globe temperature and the air temperature is ≤2℃. Summer mode: maintain an air temperature of 23-26℃, using radiation + displacement ventilation compound control; winter mode: achieve 20-24℃ temperature control through floor heating and fresh air preheating; humidity balance: use solution humidity control technology to maintain a 40-60% RH range; establish a Twall-Tdew real-time monitoring system, set a 1℃ safety margin, use a fuzzy control algorithm, and start protection measures in stages when the difference approaches the threshold, and combine the building's thermal inertia to predict the risk of condensation in the next 2 hours. The difference between the black globe temperature and the air temperature is controlled within 1.5℃, the annual condensation accident rate is reduced by more than 90%, and the thermal comfort satisfaction rate of personnel is increased to 92%.

[0078] In one of the solutions of the present invention, preferably, the top plate radiation cooling system modeling includes:

[0079] Dynamic calculation of cooling capacity: based on real-time acquisition of the water supply temperature T of the ceiling radiation cooling system supply , unit ℃, return water temperature T return , unit ℃; circulating water flow m water , unit kg / s; and water specific heat capacity at constant pressure C p Unit: kJ / (kg·K), calculate the real-time cooling capacity Q through the heat balance equation rad :

[0080] Q rad =a 10 ·m water ·c p ·(T return -T supply )

[0081] Among them, a 10 is the correction factor for the radiation system, which is between 0.9 and 1.1 and is used to calibrate the heat transfer loss in the pipeline and the non-uniform heat transfer effect at the end;

[0082] Top plate radiation surface heat transfer model: Combine the top plate wall temperature Twall, unit: ℃ and the black ball temperature T black , unit: ℃ Establish the equivalent heat transfer model between the radiation surface and the indoor environment:

[0083] Q rad，eff =U eq ·A·(T wall -T black )

[0084] Where U eq =k1·(T black -T air )+k2, is the dynamic equivalent heat transfer coefficient, unit: W / (m 2 ·K); k1, and k2 are determined by fitting experimental data, A is the radiation surface area, unit: m 2 , Q rad，eff is the actual effective cooling capacity;

[0085] Linkage with the heat pump system: water supply temperature T on the evaporator side of the heat pump system evap,supply , unit: ℃ and return water temperature T evap,return , unit: ℃, real-time calculation of heat pump cooling capacity Q HP , unit: kW:

[0086] Q HP =m HP ·c p ·(T evap，return -T evap，supply )

[0087] Among them, m HP Represents the heat pump circulating water flow rate, unit: kg / s; parameter Q HP Used to calibrate the consistency between the cooling capacity of the radiation system and the output of the heat pump to avoid system overshoot;

[0088] Among them, Q rad，reff ≤W rad , and if Q rad，eff >Q HP , indicating that the heat pump is insufficient, then reduce the water supply temperature of the radiation system or increase the water flow; if Q rad，eff <Q HP , indicating that the heat pump is over-supplied, so the water supply temperature should be increased or the water flow rate should be reduced.

[0089] Equivalent heat transfer coefficient: correction coefficient for combined radiation and convection heat transfer. Heat pump energy ratio: ratio of actual cooling capacity to input power. Pipeline heat transfer loss: heat loss rate of circulating water during transportation. With this solution, the cooling capacity calculation error is controlled within ±5%, the heat pump operating efficiency is increased by 18%, and the top plate temperature uniformity reaches ±0.8℃.

[0090] In the above scheme, as a preferred embodiment, the independent fresh air dehumidification system modeling includes:

[0091] Dynamic dehumidification capacity calculation: based on the water inlet temperature T of the independent fresh air dehumidification system cool，in Unit: ℃, water outlet temperature T cool，out Unit: ℃; air volume m air , unit kg / s, and indoor air humidity d in , unit: g / kg, outdoor air humidity dout , unit g / kg, construct dehumidification model:

[0092] W dehum =a 20 ·m air ·(d in -d out )

[0093] Among them, a 20 W is the surface cooler efficiency correction factor, which is between 1.0 and 1.05 and is used to compensate for the effects of frost or dirt on the heat exchanger surface. dehum is the dehumidification capacity, unit: g / s, which means the mass of water removed per unit time;

[0094] Sensible cooling capacity calculation:

[0095] Q fan =m air ·c p，air ·(T in -T out )

[0096] In the formula, c p，air is the specific heat capacity of air, which is 1.005 kU / (kg·K), T in T out are the air temperatures before and after treatment, in ℃, Q fan The sensible cooling capacity, unit: W, represents the sensible cooling capacity provided by the fresh air system through cooling;

[0097] Dynamic control of condensation risk: real-time monitoring of air dew point temperature T dew and top wall temperature T wall , when T wall -T dew When the temperature is ≤1℃, the anti-condensation strategy is triggered: the outlet water temperature of the surface cooler is increased by 2-3℃, and the fresh air supply volume is reduced by 10%-15%.

[0098] Surface cooler efficiency correction coefficient: dynamic compensation parameter considering the effect of scaling; air humidity difference: the difference in air humidity before and after treatment; sensible heat cooling capacity: the cooling capacity transferred by air cooling. With this solution, the dehumidification capacity calculation error is ≤±3%, the sensible heat cooling response time is shortened to 15 seconds, and the condensation accident rate is reduced to 0.3 times / year.

[0099] In one embodiment of the present invention, preferably, the separation optimization of sensible heat and wet load is achieved by the following equation:

[0100]

[0101] Among them, Q totalis the total sensible heat load, representing the total sensible heat cooling load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; Q rad is the real-time cooling capacity of the ceiling radiation cooling system; Q fan Q is the sensible heat cooling capacity of the independent fresh air dehumidification system; design is the design sensible heat load, which represents the theoretical maximum sensible heat cooling load under the system design condition; and W total is the total wet load, representing the total wet load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; W dehum is the dehumidification capacity of the independent fresh air dehumidification system; W infiltration W is the infiltration moisture load, which represents the moisture that penetrates from the outside due to insufficient air tightness of the building; design is the design wet load, which represents the theoretical maximum wet load under the system design conditions.

[0102] Total sensible heat load: the sum of all sensible heat sources of the building; infiltration moisture load: the amount of moisture entering through the gaps in the enclosure structure; design load: the theoretical load value that meets the maximum working condition. With the solution of the present invention, the load distribution response time is ≤30 seconds, the design load matching degree is more than 95%, and the system energy consumption is reduced by 22%.

[0103] In one of the schemes of the present invention, preferably, the real-time adjustment of the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system comprises the following steps:

[0104] The MPC optimization objective function is defined as minimizing the total energy consumption of the system:

[0105] min(W HP +W pump +W fan )

[0106] Among them, the heat pump energy consumption W HP , water pump energy consumption W pump , fan energy consumption W fan Respectively with the heat pump cooling capacity Q HP , circulating water flow m water , air supply volume m air Positive correlation;

[0107] Solve the optimization problem in the rolling time domain and dynamically adjust the control variables:

[0108] When the sensible heat load ratio is less than 70%, reduce the water supply temperature T of the top plate radiation system. supply , improve the actual effective cooling capacity Q rad,eff ;

[0109] When the wet load ratio is less than 90%, reduce the fresh air supply temperature T fan , improve the dehumidification capacity of the independent fresh air dehumidification system W dehum;

[0110] When T is detected wall -T dew ≤1℃, trigger the anti-condensation strategy: increase T supply 1–2℃, reduce radiant cooling; increase T fan 2–3°C, reduce dehumidification priority;

[0111] Output optimized water supply temperature T supply and supply air temperature T fan , real-time control of the roof radiation cooling and independent fresh air dehumidification system operation. With this solution, the total energy consumption of the system is reduced by 28%, the load distribution deviation is ≤5%, and the anti-condensation response time is <10 seconds.

[0112] In the above scheme, as a preferred embodiment, in the step of solving the optimization problem in the rolling time domain and dynamically adjusting the control variables: after the anti-condensation strategy is triggered, priority is given to ensuring T wall ≥T dew +1 degree Celsius, and then redistribute the heat and humidity load through MPC. With this solution, the response time to condensation accidents is shortened to 8 seconds, the load recovery time is ≤ 2 minutes, and the system stability is improved by 40%.

[0113] In one of the solutions of the present invention, as a preferred embodiment, a penalty term λ1·max(0,70%-R sen，rad ), and λ2·max(0,90%-R hum，fan ), enforcing load distribution constraints;

[0114] The weight coefficients λ1 and λ2 are dynamically adjusted according to the outdoor temperature and humidity: λ2 increases in high humidity weather, and λ1 increases in high temperature weather;

[0115] Among them, R sen,rad : The proportion of sensible heat load borne by the ceiling radiation system; R hum,fan :Wet load ratio of independent fresh air dehumidification system, value range: 0.5≤λ1≤3.0, 0.5≤λ2≤3.0. With this solution, load distribution deviation is ≤3%, system adaptability is improved by 35%, and comprehensive energy efficiency ratio is improved by 25%.

[0116] In one of the schemes of the present invention, preferably, the water supply temperature adjustment range is 18-22°C, and the air supply temperature adjustment range is 12-16°C; when the anti-condensation strategy is executed, the air supply temperature is allowed to temporarily exceed the lower limit to 10°C, but the duration is ≤5 minutes.

[0117] In one of the schemes of the present invention, as a preference, it also includes: a high-temperature cold source is directly connected to a top plate radiation cooling system, and a low-temperature cold source is connected to an independent fresh air dehumidification system.

[0118] In order to enable those skilled in the art to better understand the technical solution of the present invention, the following embodiments are now provided for further explanation:

[0119] A comprehensive control method for the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system is proposed. By real-time acquisition of system parameters and indoor environmental parameters, a system model is established. The heat and moisture load collaborative allocation and model predictive control (MPC) strategy are adopted to achieve the separation and optimization of sensible heat and moisture loads. Under the premise of meeting the requirements of indoor comfort and condensation risk, the system energy consumption is minimized. The specific steps include:

[0120] 1. Data Collection

[0121] Real-time collection of building system parameters and indoor environmental parameters, including the supply and return water temperature of the ceiling radiation cooling system, the inlet and outlet water temperature of the independent fresh air dehumidification system, and the supply and return water temperature of the evaporator side of the heat pump system; the indoor environmental parameters include the ceiling wall temperature, indoor air humidity and black globe temperature; data collection is performed using a distributed sensor network, as follows:

[0122] PT100 temperature sensor (accuracy ±0.1℃) monitors the supply and return water temperatures.

[0123] An ultrasonic flow meter (accuracy ±1.5%) measures the water flow.

[0124] Capacitive humidity sensor (accuracy ±3% RH) detects air humidity.

[0125] A black globe thermometer (accuracy ±0.5°C) is used to obtain comprehensive thermal environment parameters.

[0126] 2. Modeling

[0127] Based on the real-time data collected, model the ceiling radiation cooling system and the independent fresh air dehumidification system;

[0128] 1) Modeling of ceiling radiation cooling system includes:

[0129] Dynamic calculation of cooling capacity: based on real-time acquisition of the water supply temperature T of the ceiling radiation cooling system supply , unit ℃, return water temperature T return , unit ℃; circulating water flow m water , unit kg / s; and water specific heat capacity at constant pressure C p Unit: kJ / (kg·K), calculate the real-time cooling capacity Q through the heat balance equation rad :

[0130] Q rad =a 10 ·m water ·c p ·(T return-T supply )

[0131] Among them, a 10 is the correction factor for the radiation system, which is between 0.9 and 1.1 and is used to calibrate the heat transfer loss in the pipeline and the non-uniform heat transfer effect at the end;

[0132] Top plate radiation surface heat transfer model: Combine the top plate wall temperature Twall, unit: ℃ and the black ball temperature T black , unit: ℃ Establish the equivalent heat transfer model between the radiation surface and the indoor environment:

[0133] Q rad，eff =U eq ·A·(T wall -T black )

[0134] Where U eq =k1·(T black -T air )+k2, is the dynamic equivalent heat transfer coefficient, unit: W / (m 2 ·K); k1, and k2 are determined by fitting experimental data, A is the radiation surface area, unit: m 2 , Q rad，eff is the actual effective cooling capacity;

[0135] Linkage with the heat pump system: water supply temperature T on the evaporator side of the heat pump system evap,supply , unit: ℃ and return water temperature T evap,return , unit: ℃, real-time calculation of heat pump cooling capacity Q HP , unit: kW:

[0136] Q HP =m HP ·c p ·(T evap，return -T evap，supply )

[0137] Among them, m HP Represents the heat pump circulating water flow rate, unit: kg / s; parameter Q HP Used to calibrate the consistency between the cooling capacity of the radiation system and the output of the heat pump to avoid system overshoot;

[0138] Among them, Q rad，eff ≤Q rad , and if Q rad，eff >Q HP , indicating that the heat pump is insufficient, then reduce the water supply temperature of the radiation system or increase the water flow; if Q rad，eff <Q HP , indicating that the heat pump is over-supplied, so the water supply temperature should be increased or the water flow rate should be reduced.

[0139] 2) Independent fresh air dehumidification system modeling includes:

[0140] Dynamic dehumidification capacity calculation: based on the water inlet temperature T of the independent fresh air dehumidification system cool，in Unit: ℃, water outlet temperature T cool，out Unit: ℃; air volume m air , unit kg / s, and indoor air humidity d in , unit: g / kg, outdoor air humidity d out , unit g / kg, construct dehumidification model:

[0141] W dehum =a 20 ·m air ·(d in -d out )

[0142] Among them, a 20 W is the surface cooler efficiency correction factor, which is between 1.0 and 1.05 and is used to compensate for the effects of frost or dirt on the heat exchanger surface. dehum is the dehumidification capacity, unit: g / s, which means the mass of water removed per unit time;

[0143] Sensible cooling capacity calculation:

[0144] Q fan =m air ·c p，air ·(T in -T out )

[0145] In the formula, c p，air is the specific heat capacity of air, which is 1.005 kU / (kg·K), T in T out are the air temperatures before and after treatment, in ℃, Q fan The sensible cooling capacity, unit: W, represents the sensible cooling capacity provided by the fresh air system through cooling;

[0146] Dynamic control of condensation risk: real-time monitoring of air dew point temperature T dew and top wall temperature T wall , when T wall -T dew When the temperature is ≤1℃, the anti-condensation strategy is triggered: the outlet water temperature of the surface cooler is increased by 2-3℃, and the fresh air supply volume is reduced by 10%-15%.

[0147] 3. Coordinated distribution of heat and humidity loads

[0148] Based on the law of coordinated distribution of heat and moisture loads, the separation and optimization of sensible heat and moisture loads are achieved through dynamic constraints, so that the sensible heat load is dominated by the ceiling radiation cooling system, and the moisture load is dominated by the independent fresh air dehumidification system; the dominant strategy for sensible heat load and moisture load is: the proportion of sensible heat load borne by the ceiling radiation cooling system is ≥70%; the proportion of moisture load borne by the independent fresh air dehumidification system is ≥90%.

[0149] The separation optimization of sensible heat and wet load is achieved through the following equation:

[0150]

[0151] Among them, Q total is the total sensible heat load, representing the total sensible heat cooling load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; Q rad is the real-time cooling capacity of the ceiling radiation cooling system; Q fan Q is the sensible heat cooling capacity of the independent fresh air dehumidification system; design is the design sensible heat load, which represents the theoretical maximum sensible heat cooling load under the system design condition; and

[0152] W total is the total wet load, representing the total wet load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; W dehum is the dehumidification capacity of the independent fresh air dehumidification system; W infiltration W is the infiltration moisture load, which represents the moisture that penetrates from the outside due to insufficient air tightness of the building; design is the design wet load, which represents the theoretical maximum wet load under the system design conditions.

[0153] 4. Model Predictive Control

[0154] According to the radiation cooling system model and the fresh air dehumidification system model, as well as the sensible heat load and wet load dominant strategy, the model predictive control MPC strategy is adopted to minimize energy consumption while meeting the indoor comfort and condensation risk standards, and adjust the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system in real time.

[0155] Real-time adjustment of the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system includes the following steps:

[0156] The MPC optimization objective function is defined as minimizing the total energy consumption of the system:

[0157] min(W HP +W pump +W fan )

[0158] Among them, the heat pump energy consumption W HP , water pump energy consumption W pump , fan energy consumption Wfan Respectively with the heat pump cooling capacity Q HP , circulating water flow m water , air supply volume m air Positive correlation;

[0159] Solve the optimization problem in the rolling time domain and dynamically adjust the control variables:

[0160] When the sensible heat load ratio is less than 70%, reduce the water supply temperature T of the top plate radiation system. supply , improve the actual effective cooling capacity Q rad,eff ;

[0161] When the wet load ratio is less than 90%, reduce the fresh air supply temperature T fan , improve the dehumidification capacity of the independent fresh air dehumidification system W dehum ;

[0162] When T is detected wall -T dew ≤1℃, trigger the anti-condensation strategy: increase T supply 1–2℃, reduce radiant cooling; increase T fan 2–3°C, reduce dehumidification priority;

[0163] Solve the optimization problem in the rolling time domain and dynamically adjust the control variables: After the anti-condensation strategy is triggered, T is prioritized. wall ≥T dew +1 degree Celsius, and then redistribute the heat and moisture load through MPC.

[0164] Introducing the penalty term λ1·max(0,70%-R sen，rad ), and λ2·max(0,90%-R hum，fan ), enforcing load distribution constraints;

[0165] The weight coefficients λ1 and λ2 are dynamically adjusted according to the outdoor temperature and humidity: λ2 increases in high humidity weather, and λ1 increases in high temperature weather;

[0166] Among them, R sen,rad : The proportion of sensible heat load borne by the ceiling radiation system; R hum,fan : The wet load ratio of the independent fresh air dehumidification system, the value range is: 0.5≤λ1≤3.0, 0.5≤λ2≤3.0.

[0167] Output optimized water supply temperature T supply and supply air temperature T fan , real-time control of the operation of the ceiling radiation cooling and independent fresh air dehumidification system. The water supply temperature adjustment range is 18-22℃, and the supply air temperature adjustment range is 12-16℃; when the anti-condensation strategy is implemented, the supply air temperature is allowed to temporarily exceed the lower limit to 10℃, but the duration is ≤5 minutes.

[0168] The condensation risk level meets the standard when the probability of the condensation risk threshold is ≤4-6%; the indoor comfort standards include: indoor air temperature: 23–26℃ in summer and 20–24℃ in winter; indoor air humidity: 40%–60% RH; the difference between the black globe temperature and the air temperature is ≤2℃.

[0169] The high-temperature cold source is directly connected to the roof radiation cooling system, and the low-temperature cold source is connected to the independent fresh air dehumidification. The cold source system design is as follows:

[0170] The high temperature system uses a ground source heat pump + energy storage tank.

[0171] The low temperature system is equipped with a solution humidification unit.

[0172] Establish a cooling source priority matrix, pre-start the cooling source based on load forecasting, trigger cooling source switching according to temperature thresholds, and achieve combined control of multiple cooling sources through energy efficiency optimization.

[0173] Through this embodiment, the system energy efficiency ratio can be improved by more than 30%, the indoor temperature and humidity fluctuations can be controlled within the range of ±0.5℃ / ±5%RH, the condensation risk probability is stabilized below the 4-6% threshold, the personnel thermal comfort satisfaction rate is increased to 92%, the equipment life is extended by 15%, and the comprehensive energy saving rate can reach 32%.

[0174] The number of devices and processing scales described here are used to simplify the description of the present invention. Applications, modifications and variations of the present invention will be obvious to those skilled in the art.

[0175] Although the embodiments of the present invention have been disclosed as above, they are not limited to the applications listed in the specification and the implementation modes. They can be fully applied to various fields suitable for the present invention. For those familiar with the art, additional modifications can be easily implemented. Therefore, without departing from the general concept defined by the claims and the scope of equivalents, the present invention is not limited to the specific details and the embodiments shown and described herein.

Claims

1. A comprehensive control method for mixed operation of ceiling radiation cooling and independent fresh air dehumidification system, characterized in that: The steps include: Real-time collection of building system parameters and indoor environmental parameters, including supply and return water temperature of the ceiling radiation cooling system, inlet and outlet water temperature of the independent fresh air dehumidification system, and supply and return water temperature of the evaporator side of the heat pump system; indoor environmental parameters including ceiling wall temperature, indoor air humidity and black globe temperature; Based on the real-time data collected, model the ceiling radiation cooling system and the independent fresh air dehumidification system; Based on the heat and moisture load coordinated distribution rule, the separation and optimization of sensible heat and moisture loads are achieved through dynamic constraints, so that the sensible heat load is dominated by the ceiling radiation cooling system, and the moisture load is dominated by the independent fresh air dehumidification system; Based on the radiation cooling system model and the fresh air dehumidification system model, as well as the sensible heat load and wet load dominant strategy, the model predictive control MPC strategy is adopted to minimize energy consumption while meeting the indoor comfort and condensation risk standards, and adjust the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system in real time; Among them, the dominant strategies for sensible heat load and wet load are: the ceiling radiation cooling system bears a proportion of sensible heat load ≥ 70%; the independent fresh air dehumidification system bears a proportion of wet load ≥ 90%.

2. The method for controlling the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system according to claim 1, characterized in that: The condensation risk level meets the standard when the probability of condensation risk threshold is ≤4-6%; Indoor comfort standards include: indoor air temperature: 23–26°C in summer, 20–24°C in winter; indoor air humidity: 40%–60% RH; the difference between the black globe temperature and the air temperature ≤ 2°C.

3. The method for controlling the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system according to claim 1, characterized in that: Modeling of ceiling radiant cooling systems includes: Dynamic calculation of cooling capacity: based on real-time acquisition of the water supply temperature T of the ceiling radiation cooling system supply , unit ℃, return water temperature T return , unit ℃; circulating water flow m water , unit kg / s; and water specific heat capacity at constant pressure C p Unit: kJ / (kg·K), calculate the real-time cooling capacity Q through the heat balance equation rad : Q rad =a 10 ·m water ·c p ·(T return -T supply ) Among them, a 10 is the correction factor for the radiation system, which is between 0.9 and 1.1 and is used to calibrate the heat transfer loss in the pipeline and the non-uniform heat transfer effect at the end; Top plate radiation surface heat transfer model: Combine the top plate wall temperature Twall, unit: ℃ and the black ball temperature T black , unit: ℃ Establish the equivalent heat transfer model between the radiation surface and the indoor environment: Q rad，eff =U eq ·A·(T wall -T black ) Where U eq =k1·(T black -T air )+k2, is the dynamic equivalent heat transfer coefficient, unit: W / (m 2 ·K); k1, and k2 are determined by fitting experimental data, A is the radiation surface area, unit: m 2 , Q rad，eff is the actual effective cooling capacity; Linkage with the heat pump system: water supply temperature T on the evaporator side of the heat pump system evap,supply , unit: ℃ and return water temperature T evap,return , unit: ℃, real-time calculation of heat pump cooling capacity Q HP , unit: kW: Q HP =m HP ·c p ·(T evap，return -T evap，supply ) Among them, m HP Represents the heat pump circulating water flow rate, unit: kg / s; parameter Q HP Used to calibrate the consistency between the cooling capacity of the radiation system and the output of the heat pump to avoid system overshoot; Among them, Q rad，eff ≤Q rad , and if Q rad，eff >Q HP , indicating that the heat pump is insufficient, then reduce the water supply temperature of the radiation system or increase the water flow; if Q rad，eff <Q HP , indicating that the heat pump is over-supplied, so the water supply temperature should be increased or the water flow rate should be reduced.

4. The method for controlling the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system according to claim 3, characterized in that: Independent fresh air dehumidification system modeling includes: Dynamic dehumidification capacity calculation: based on the water inlet temperature T of the independent fresh air dehumidification system cool，in Unit: ℃, water outlet temperature T cool，out Unit: ℃; air volume m air , unit kg / s, and indoor air humidity d in , unit: g / kg, outdoor air humidity d out , unit g / kg, construct dehumidification model: W dehum =a 20 ·m air ·(d in -d out ) Among them, a 20 W is the surface cooler efficiency correction factor, which is between 1.0 and 1.05 and is used to compensate for the effects of frost or dirt on the heat exchanger surface. dehum is the dehumidification capacity, unit: g / s, which means the mass of water removed per unit time; Sensible cooling capacity calculation: Q fan =m air ·c p，air ·(T in -T out ) In the formula, c p，air is the specific heat capacity of air, which is 1.005 kU / (kg·K), T in T out are the air temperatures before and after treatment, in ℃, Q fan The sensible cooling capacity, unit: W, represents the sensible cooling capacity provided by the fresh air system through cooling; Dynamic control of condensation risk: real-time monitoring of air dew point temperature T dew and top wall temperature T wall , when T wall -T dew When the temperature is ≤1℃, the anti-condensation strategy is triggered: the outlet water temperature of the surface cooler is increased by 2-3℃, and the fresh air supply volume is reduced by 10%-15%.

5. The method for controlling the mixed operation of the ceiling radiation cooling and the independent fresh air dehumidification system according to claim 1, characterized in that: The optimization of the separation of sensible heat and moisture load is achieved by the following equation: Among them, Q total is the total sensible heat load, representing the total sensible heat cooling load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; Q rad is the real-time cooling capacity of the ceiling radiation cooling system; Q fan Q is the sensible heat cooling capacity of the independent fresh air dehumidification system; design is the design sensible heat load, which represents the theoretical maximum sensible heat cooling load under the system design condition; and W total is the total wet load, representing the total wet load that the ceiling radiation cooling and independent fresh air dehumidification system need to bear; W dehum is the dehumidification capacity of the independent fresh air dehumidification system; W infiltration W is the infiltration moisture load, which represents the moisture that penetrates from the outside due to insufficient air tightness of the building; design is the design wet load, which represents the theoretical maximum wet load under the system design conditions.

6. The method for controlling the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system according to claim 4, characterized in that: Real-time adjustment of the water supply temperature of the ceiling radiation cooling system and the air supply temperature of the fresh air dehumidification system includes the following steps: The MPC optimization objective function is defined as minimizing the total energy consumption of the system: min(in HP +W pump +W fan ) Among them, the heat pump energy consumption W HP , water pump energy consumption W pump , fan energy consumption W fan Respectively with the heat pump cooling capacity Q HP , circulating water flow m water , air supply volume m air Positive correlation; Solve the optimization problem in the rolling time domain and dynamically adjust the control variables: When the sensible heat load ratio is less than 70%, reduce the water supply temperature T of the top plate radiation system. supply , improve the actual effective cooling capacity Q rad,eff ; When the wet load ratio is less than 90%, reduce the fresh air supply temperature T fan , improve the dehumidification capacity of the independent fresh air dehumidification system W dehum ; When T is detected wall -T dew ≤1℃, trigger the anti-condensation strategy: increase T supply 1–2℃, reduce radiant cooling; increase T fan 2–3°C, reduce dehumidification priority; Output optimized water supply temperature T supply and supply air temperature T fan , real-time regulation of ceiling radiation cooling and independent fresh air dehumidification system operation.

7. The method for controlling the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system according to claim 6, characterized in that: Solve the optimization problem in the rolling time domain and dynamically adjust the control variables: After the anti-condensation strategy is triggered, T is prioritized. wall ≥T dew +1 degree Celsius, and then redistribute the heat and moisture load through MPC.

8. The method for controlling the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system according to claim 6, characterized in that: Introducing the penalty term λ1·max(0,70%-R sen，rad ), and λ2·max(0,90%-R hum，fan ), enforcing load distribution constraints; The weight coefficients λ1 and λ2 are dynamically adjusted according to the outdoor temperature and humidity: λ2 increases in high humidity weather, and λ1 increases in high temperature weather; Among them, R sen,rad : The proportion of sensible heat load borne by the ceiling radiation system; R hum,fan : The wet load ratio of the independent fresh air dehumidification system, the value range is: 0.5≤λ1≤3.0, 0.5≤λ2≤3.

0.

9. The method for controlling the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system according to claim 4, characterized in that: The water supply temperature adjustment range is 18–22°C, and the supply air temperature adjustment range is 12–16°C. When the anti-condensation strategy is implemented, the supply air temperature is allowed to temporarily exceed the lower limit to 10°C, but the duration is ≤5 minutes.

10. The method for controlling the mixed operation of ceiling radiation cooling and independent fresh air dehumidification system according to claim 1, characterized in that: Also includes: The high-temperature cold source is directly connected to the ceiling radiation cooling system, and the low-temperature cold source is connected to the independent fresh air dehumidification.

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