CN115183352A - PMV-based buried pipe direct supply floor radiation cooling control method and device - Google Patents

PMV-based buried pipe direct supply floor radiation cooling control method and device Download PDF

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CN115183352A
CN115183352A CN202210933300.XA CN202210933300A CN115183352A CN 115183352 A CN115183352 A CN 115183352A CN 202210933300 A CN202210933300 A CN 202210933300A CN 115183352 A CN115183352 A CN 115183352A
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pmv
air
indoor
floor
temperature
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CN115183352B (en
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刘吉营
任婧
苏蒙
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Shandong Jianzhu University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/61—Control or safety arrangements characterised by user interfaces or communication using timers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/20—Humidity
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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Abstract

The invention discloses a PMV-based buried pipe direct supply floor radiation cooling control method and a PMV-based buried pipe direct supply floor radiation cooling control device, wherein the control method comprises the following steps of: collecting indoor environment parameters such as floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature, setting clothes thermal resistance and personnel activity intensity as fixed values, and calculating PMV values; predicting a PMV value by adopting an indoor environment dynamic heat and humidity model; setting a control rule for the operation of a cooling system by taking the lowest energy consumption of a floor radiation and ventilation composite cooling system as a target function and taking an indoor comfort index PMV threshold range as a constraint condition; and determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value. The invention improves the regulation efficiency and the accuracy by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system.

Description

PMV-based buried pipe direct supply floor radiation cooling control method and device
Technical Field
The invention relates to a PMV index-based buried pipe direct supply floor radiation cooling control method and device, and belongs to the technical field of air conditioner optimization control.
Background
The direct radiation cooling of the ground buried pipe for the floor is considered as a non-ideal cooling mode by people at present, the temperature of the floor is controlled to be more than 18-20 ℃, the feeling of cold feet can not be generated in summer, and the requirement of thermal comfort is met. The existing floor radiation and ventilation composite cooling system mainly adopts a temperature-based control method without considering personnel heat sensation and other indoor environment parameters. Because the radiation plate surface realizes heat transfer through radiation heat transfer and convection heat transfer mode, so compare with traditional convection current mode, the thermal comfort under the radiation cooling mode has difference to some extent for indoor temperature setpoint control is difficult to satisfy thermal comfort demand. Most control technologies respectively adjust the water supply flow and the water supply temperature of the floor radiation system and the air supply quantity and the air supply temperature of the ventilation system, and do not consider the interaction and the internal relation in the cooling process of the two systems, so that the energy efficiency and the control effect of the composite cooling system are poor.
The PMV value is an evaluation index for characterizing the thermal response (thermal sensation) of the human body proposed by professor Fan Geer (p.o. Fanger) in denmark, and represents the average of the thermal sensations of most people in the same environment. The PMV value can be obtained by estimating the metabolic rate of human body activity and the heat insulation value of the clothes, and the following environmental parameters are required: air temperature, average radiant temperature, relative air flow rate, and air humidity. Relevant researches show that PMV-based control comprehensively considers human activity intensity, clothes thermal resistance, air temperature, average radiation temperature, air flow speed and air humidity, can accurately reflect direct physiological and psychological reactions of human bodies to indoor thermal environments, and is an effective control method for improving indoor thermal comfort and reducing energy consumption. In addition, the cold load borne by the ventilation system is proved to be a key control parameter of the composite cold supply system in the ratio of the total cold load. Therefore, the load bearing proportion of the two systems is reasonably adjusted, and the cooling capacity and the energy-saving potential of the systems can be improved.
The indoor thermal comfort index PMV is widely used for evaluating indoor thermal comfort created by a composite cooling system, the application space of the PMV is limited, the PMV is necessary to be introduced into a control process to replace indoor temperature and humidity parameters and serve as new judgment parameters, parallel monitoring control of indoor temperature and humidity is achieved, and an accurate and effective system regulation scheme is implemented. However, research on the duty ratio of floor radiating systems to ventilation systems has been limited to describing the change in duty ratio during cooling or to proposing a particular range of duty ratios that improves the energy efficiency of the system.
Disclosure of Invention
In order to solve the problems of low energy efficiency and poor control effect of a composite cooling system caused by a traditional control method, the invention provides a PMV index-based buried pipe direct supply floor radiation cooling control method and device, which can improve the regulation and control efficiency and accuracy of a floor radiation and ventilation composite cooling system.
The technical scheme adopted for solving the technical problems is as follows:
on one hand, the PMV-based buried pipe direct supply floor radiation cooling control method provided by the embodiment of the invention comprises the following steps:
collecting indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values, and calculating a PMV value; the indoor environmental parameters comprise floor surface temperature, dry-bulb temperature, relative humidity, air flow rate and average radiation temperature;
predicting a PMV value by adopting an indoor environment dynamic heat and humidity model;
setting a control rule for the operation of a cooling system by taking the lowest energy consumption of a floor radiation and ventilation composite cooling system as a target function and taking an indoor comfort index PMV threshold range as a constraint condition;
and determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
As a possible implementation manner of this embodiment, the PMV threshold range is [ -0.5, 0.5].
As a possible implementation manner of this embodiment, the PMV value is calculated as:
Figure 572941DEST_PATH_IMAGE001
Figure 841111DEST_PATH_IMAGE002
Figure DEST_PATH_IMAGE003
Figure 410501DEST_PATH_IMAGE004
Figure DEST_PATH_IMAGE005
in the formula (I), the compound is shown in the specification,t a dry ball temperature, ° C;RHrelative humidity,%;v a is the air flow rate, m/s;t r mean radiation temperature, ° C;I cl is the garment thermal resistance, clo;Mhuman activity intensity, W; w is the mechanical work done by the human body, and is zero when sitting still, J;P a the partial pressure of water vapor of air around a human body is Pa;f cl is the dressing area coefficient;t cl the temperature of the outer surface of the clothes is ° C;h c is the convective heat transfer coefficient, W/(m) 2 ∙K)。
As a possible implementation manner of this embodiment, the predicting the PMV value by using the indoor environment dynamic heat and humidity model includes:
predicting dry bulb temperature by utilizing indoor environment dynamic heat and humidity modelt a Relative humidity ofRH'Ping' for preventing and curing fractureMean radiant temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises the following components:
Figure 637083DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,C i is the heat capacity of the air node, J/K;T i is the air node temperature, K;Q surf,i gain of radiant and convective heat on the surface of the enclosure, W;Q env,i is the heat transferred to the air node through the wall, W;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain (generated by personnel, equipment, lighting, etc.), W;Q solar,i to gain solar radiant heat through the window, W;Q r,i providing cold energy, W, for the floor radiation system to the air node;Q v,i providing cold energy, W, for the ventilation system to the air node;
Figure DEST_PATH_IMAGE007
in the formula (I), the compound is shown in the specification,M eff,i the effective moisture capacity of the air node is g/g;ω i is the air node moisture content, g;W inf,i moisture gain due to permeated air, g;W int,i gain in indoor moisture content, g;W env the moisture content g is transferred to the air node through the wall; W v,i the moisture removed for the vent system, g;
before the working start time of personnel, the gain of indoor heat and moisture content is approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture content needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
As a possible implementation manner of this embodiment, the objective optimization function is:
Figure 675447DEST_PATH_IMAGE008
Figure DEST_PATH_IMAGE009
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump, kWh;ρ sw for the water density, kg/m 3 ；gIs the acceleration of gravity, m/s 2 ；HM is the lift of the circulating water pump;V sw for volume flow of water supply, m 3 /h；η pump The efficiency of the circulating water pump;E fan kWh is the fan energy consumption;DPis the fan pressure drop, pa;ρ a is the blast density in kg/m 3 ；V sa For volume flow of air supply, m 3 /s；η fan The fan efficiency; T out outdoor air temperature, deg.C;T set set point temperature, ° C;T out,dew the dew point temperature of outdoor air, C; dh v Is the enthalpy of evaporation, J/kg;ω out the moisture content of outdoor air is g/kg;ω max is the maximum moisture content set point, g/kg.
The constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
As a possible implementation manner of this embodiment, the determining the opening time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load carrying ratio of the ventilation system and the floor radiation system according to the interval where the PMV value is located includes:
according to the moisture content to be removed indoors and the design air supply temperature and the design air supply quantity of the ventilation system, calculating the pre-dehumidification time required by the ventilation system, and determining the starting time of the ventilation system:
Figure 498040DEST_PATH_IMAGE010
in the formula (I), the compound is shown in the specification,tpre-dehumidification time h is needed for a ventilation system;V sa for volume flow of air supply, m 3 /h；WThe moisture content, g, to be removed indoors;d in is the moisture content of indoor air, g/kg;d sa is the air supply moisture content, g/kg.
When the surface temperature of the floor is higher than the dew point temperature, the floor radiation system is started;
before the working time of the personnel, according to the predicted interval of PMV value corresponding to the working starting time of the personnel, the sensible heat load bearing proportion S of the ventilation system and the floor radiation system is adjusted v /S R Determining the optimal water supply flow, air supply temperature and air supply quantity which meet the PMV threshold requirement and have the lowest energy consumption;
during the working time of the personnel, S is adjusted according to the predicted PMV value interval after 10 minutes at the current moment v /S R And determining the optimal air supply temperature and air supply quantity.
As a possible implementation manner of this embodiment, the staff working time period is 9 to 00; the floor radiation system and ventilation system off time was 17.
As a possible implementation manner of this embodiment, the sensible heat load bearing ratio S of the ventilation system and the floor radiation system is adjusted v /S R Expressed as:
Figure DEST_PATH_IMAGE011
in the formula (I), the compound is shown in the specification,Q vent. in order to replace the sensible heat load borne by a ventilation system, kW ∙ h;Q RFC the sensible heat load borne by a floor radiation system is kW ∙ h;T in indoor air temperature, ° C;T sa the temperature of the air supply is equal to DEG C;Ais the floor surface area, m 2 ；h t Is the total heat transfer coefficient, W/(m) 2 ∙K)；T op Operating temperature, ° C;T f the surface temperature of the floor is ° C.
As a possible implementation manner of this embodiment, the determining the optimal supply air temperature and the supply air amount includes:
at the moment of starting staff work, setting the initial operating parameters of the ventilation system: designing air supply temperature and air supply quantity, and setting initial operation parameters of a floor radiation system;
if the surface temperature of the floor does not meet the design requirement, the floor radiation cooling system operates at the maximum allowable water supply flow and is kept unchanged;
if the surface temperature of the floor reaches the design requirement, the floor radiation cooling system operates at the designed water supply flow and is maintained unchanged.
On the other hand, the PMV-based radiant cooling control device for a buried pipe direct-supply floor provided by the embodiment of the invention comprises:
the data acquisition processing module is used for acquiring indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature;
the PMV value prediction module is used for predicting the PMV value by adopting an indoor environment dynamic heat and humidity model;
the control rule setting module is used for setting a control rule for the operation of the cooling system by taking the lowest energy consumption of the floor radiation and ventilation combined cooling system as a target function and taking the indoor comfort index PMV threshold range as a constraint condition;
and the cooling system control module is used for determining the starting time of the ventilation system and the floor radiation system and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
As a possible implementation manner of this embodiment, the PMV value prediction module is specifically configured to predict the dry-bulb temperature by using an indoor environment dynamic heat and humidity modelt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises an indoor environment dynamic heat model and an indoor environment dynamic humidity model;
the indoor environment dynamic thermal model comprises the following steps:
Figure 938249DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,C i is the heat capacity of the air node, J/K;T i is the air node temperature, K;Q surf,i gain of radiant and convective heat on the surface of the enclosure, W;Q env,i w is the heat transferred to the air node through the wall;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain (generated by personnel, equipment, lighting, etc.), W;Q solar,i is the solar radiant heat gain through the window, W;Q r,i providing cold energy, W, for the floor radiation system to the air node;Q v,i providing cold energy, W, for the ventilation system to the air node;
the indoor environment dynamic wet model is as follows:
Figure 538994DEST_PATH_IMAGE007
in the formula (I), the compound is shown in the specification,M eff,i the effective moisture capacity of the air node is g/g;ω i is the air node moisture content, g;W inf,i moisture gain due to permeated air, g;W int,i gain in indoor moisture content, g;W env the moisture content g is transferred to the air node through the wall; W v,i the moisture removed for the vent system, g;
before the working start time of personnel, the gain of indoor heat and moisture content is approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture content needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
As a possible implementation manner of this embodiment, the objective optimization function is:
Figure 799074DEST_PATH_IMAGE008
Figure 392736DEST_PATH_IMAGE009
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump, kWh;ρ sw for the water density, kg/m 3 ；gIs the acceleration of gravity, m/s 2 ；HM is the lift of the circulating water pump;V sw for volume flow of water supply, m 3 /h；η pump The efficiency of the circulating water pump;E fan kWh is the fan energy consumption;DPis the fan pressure drop，Pa；ρ a Is the blast density in kg/m 3 ；V sa M is the volume flow of air supply 3 /s；η fan The fan efficiency; T out outdoor air temperature, deg.C;T set set point temperature, ° C;T out,dew the dew point temperature of outdoor air, C; dh v Is the enthalpy of evaporation, J/kg;ω out the moisture content of outdoor air is g/kg;ω max is the maximum moisture content set point, g/kg.
The constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
The technical scheme of the embodiment of the invention has the following beneficial effects:
according to the invention, the sensible heat load bearing proportion of the ventilation system and the floor radiation system is adjusted, the cooling capacity proportion of the ventilation system/the floor radiation system is increased, the directivity requirement is added for adjusting the cooling capacity of the two systems, the regulation efficiency and the accuracy of the floor radiation and ventilation composite cooling system are improved, and the problems of low energy efficiency and poor control effect of the composite cooling system caused by the traditional control method are solved.
The invention aims at the lowest energy consumption of the floor radiation and ventilation composite cooling system, and takes the indoor comfort index PMV of-0.5 and 0.5 as the constraint condition. The control method takes PMV as a judgment parameter and takes the sensible heat load bearing ratio Sv/SR of the ventilation system and the floor radiation system as a regulation parameter. PMV does not need to be controlled to be [ -0.5, 0.5] before the working start time of the personnel, so that the Sv/SR is adjusted according to the interval where the PMV value corresponding to the predicted working start time of the personnel is located, the PMV threshold requirement can be met, and the energy consumption is saved; within the working time period of personnel, the Sv/SR is adjusted according to the predicted interval of the PMV value after 10 minutes from the current moment, so that the system can respond to indoor thermal gain change in time, and the problem of response hysteresis of a floor radiation system is effectively solved. The Sv/SR method can be adjusted to determine the specific gravity change of the cooling capacity of the two systems, and the cooperative cooling effect of the two systems can be enhanced, so that the cooling capacity supply is matched with the demand, and the indoor heat and humidity load is efficiently treated. On the premise of ensuring the indoor comfort level, the invention improves the control precision and the system energy efficiency of the floor radiation and ventilation composite cooling system.
Drawings
FIG. 1 is a flow chart illustrating a PMV based method for radiant cooling of a buried pipe direct-fed floor according to an exemplary embodiment;
FIG. 2 is a block diagram of a PMV based buried pipe direct supply floor radiant cooling control apparatus according to an exemplary embodiment;
FIG. 3 is a schematic view of a composite floor radiant and ventilation cooling system according to an exemplary embodiment;
fig. 4 is a flow chart illustrating a PMV index based buried pipe direct supply floor radiant cooling control strategy according to an exemplary embodiment.
In fig. 3, 1-air supply outlet, 2-cold radiation coil, 3-air return inlet, 4-underground heat exchanger, 5-buried pipe loop circulating water pump, 6-fan, 7-surface air cooler, 8-air handling unit, and 9-fresh air inlet.
Detailed Description
The invention is further illustrated by the following examples in conjunction with the following figures:
in order to clearly explain the technical features of the present invention, the following detailed description of the present invention is provided with reference to the accompanying drawings. The following disclosure provides many different embodiments, or examples, for implementing different features of the invention. To simplify the disclosure of the present invention, specific example components and arrangements are described below. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. It should be noted that the components illustrated in the figures are not necessarily drawn to scale. Descriptions of well-known components and processing techniques and procedures are omitted so as to not unnecessarily limit the invention.
The research about the load bearing proportion of the floor radiation system and the ventilation system is limited to describing the load bearing proportion change in the cooling process or providing a specific load bearing proportion range for improving the energy efficiency of the system, the control mode of adjusting the load bearing proportion of the two systems according to the range of PMV is lacked, the cooling capacity proportion of the ventilation system/the floor radiation system is increased by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system, the requirement for adjusting the directivity of the cooling capacity of the two systems is added, and the regulation efficiency and the regulation accuracy are improved.
As shown in fig. 1, a PMV-based method for controlling radiation cooling of a buried pipe direct-supply floor according to an embodiment of the present invention includes the following steps:
collecting indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values, and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature;
predicting a PMV value by adopting an indoor environment dynamic heat and humidity model;
setting a control rule for the operation of a cooling system by taking the lowest energy consumption of a floor radiation and ventilation composite cooling system as a target function and taking an indoor comfort index PMV threshold range as a constraint condition;
and determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
As a possible implementation manner of this embodiment, the PMV threshold range is [ -0.5, 0.5].
As a possible implementation manner of this embodiment, the PMV value is calculated as:
Figure 421872DEST_PATH_IMAGE001
Figure 459098DEST_PATH_IMAGE002
Figure 940895DEST_PATH_IMAGE003
Figure 88979DEST_PATH_IMAGE004
Figure 723354DEST_PATH_IMAGE005
in the formula (I), the compound is shown in the specification,t a dry ball temperature, ° C;RHrelative humidity,%;v a is the air flow rate, m/s;t r mean radiant temperature, ° C;I cl is the garment thermal resistance, clo;Mhuman activity intensity, W; w is the mechanical work done by the human body, and is zero when sitting still, J;P a the partial pressure of water vapor of air around a human body is Pa;f cl is the dressing area coefficient;t cl the temperature of the outer surface of the clothes is DEG C;h c is the convective heat transfer coefficient, W/(m) 2 ∙K)。
As a possible implementation manner of this embodiment, the predicting the PMV value by using the indoor environment dynamic heat and humidity model includes:
predicting dry bulb temperature by utilizing indoor environment dynamic heat and humidity modelt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises the following components:
Figure 931481DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,C i is heat of air nodeCapacity, J/K;T i is the air node temperature, K;Q surf,i gain of radiant and convective heat on the surface of the enclosure, W;Q env,i is the heat transferred to the air node through the wall, W;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain (generated by personnel, equipment, lighting, etc.), W;Q solar,i is the solar radiant heat gain through the window, W;Q r,i providing cold energy, W, for the floor radiation system to the air node;Q v,i providing cold energy, W, for the ventilation system to the air node;
Figure 900575DEST_PATH_IMAGE007
in the formula (I), the compound is shown in the specification,M eff,i the effective moisture capacity of the air node is g/g;ω i is the air node moisture content, g;W inf,i moisture gain due to permeated air, g;W int,i gain in indoor moisture content, g;W env the moisture content g is transferred to the air node through the wall; W v,i the moisture removed for the vent system, g;
before the working start time of personnel, the gains of indoor heat and moisture are approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
As a possible implementation manner of this embodiment, the objective optimization function is:
Figure 586771DEST_PATH_IMAGE008
Figure 590499DEST_PATH_IMAGE009
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump, kWh;ρ sw for the water density, kg/m 3 ；gIs the acceleration of gravity, m/s 2 ；HM is the lift of the circulating water pump;V sw for volume flow of water supply, m 3 /h；η pump The efficiency of the circulating water pump;E fan kWh is the fan energy consumption;DPis the fan pressure drop, pa;ρ a is the blast density in kg/m 3 ；V sa For volume flow of air supply, m 3 /s；η fan The fan efficiency; T out outdoor air temperature, deg.C;T set set point temperature, ° C;T out,dew the dew point temperature of outdoor air, C; dh v Is the enthalpy of evaporation, J/kg;ω out is the moisture content of outdoor air, g/kg;ω max is the set value of the maximum moisture content, g/kg;
the constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
As a possible implementation manner of this embodiment, the determining the opening time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load carrying ratio of the ventilation system and the floor radiation system according to the interval where the PMV value is located includes:
according to the moisture content to be removed indoors and the design air supply temperature and the design air supply quantity of the ventilation system, calculating the pre-dehumidification time required by the ventilation system, and determining the starting time of the ventilation system:
Figure 969528DEST_PATH_IMAGE010
in the formula (I), the compound is shown in the specification,tpre-dehumidification time h required by a ventilation system;V sa for volume flow of air supply, m 3 /h；WThe moisture content, g, to be removed indoors;d in is the moisture content of indoor air, g/kg;d sa is the air supply moisture content, g/kg.
When the surface temperature of the floor is higher than the dew point temperature, the floor radiation system is started;
before the working time of the personnel, the sensible heat load bearing proportion S of the ventilation system and the floor radiation system is adjusted according to the predicted PMV value corresponding to the working start time of the personnel v /S R Determining the optimal water supply flow, air supply temperature and air supply quantity which meet the PMV threshold requirement and have the lowest energy consumption;
during the working time of the personnel, S is adjusted according to the predicted PMV value interval after 10 minutes at the current moment v /S R And determining the optimal air supply temperature and air supply quantity.
As a possible implementation manner of this embodiment, the staff working time period is 9 to 00; the floor radiation system and ventilation system off time was 17.
As a possible implementation manner of this embodiment, the sensible heat load bearing ratio S of the ventilation system and the floor radiation system is adjusted v /S R Expressed as:
Figure 698622DEST_PATH_IMAGE011
in the formula (I), the compound is shown in the specification,Q vent. in order to replace the sensible heat load borne by a ventilation system, kW ∙ h;Q RFC the sensible heat load borne by a floor radiation system is kW ∙ h;T in indoor air temperature, ° C;T sa air supply temperature, C;Ais a floorSurface area, m 2 ；h t Is the total heat transfer coefficient, W/(m) 2 ∙K)；T op Operating temperature, ° C;T f the surface temperature of the floor is ° C.
As a possible implementation manner of this embodiment, the determining the optimal supply air temperature and the supply air amount includes:
at the moment of starting staff work, setting the initial operating parameters of the ventilation system: designing air supply temperature and air supply quantity, and setting initial operation parameters of a floor radiation system;
if the surface temperature of the floor does not meet the design requirement, the floor radiation cooling system operates at the maximum allowable water supply flow and is kept unchanged;
if the surface temperature of the floor reaches the design requirement, the floor radiation cooling system operates at the designed water supply flow and is maintained unchanged.
As shown in fig. 2, an embodiment of the present invention provides a PMV-based direct-supply ground-buried-pipe-based radiant cooling control device, including:
the data acquisition processing module is used for acquiring indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature;
the PMV value prediction module is used for predicting the PMV value by adopting an indoor environment dynamic heat and humidity model;
the control rule setting module is used for setting a control rule for the operation of the cooling system by taking the lowest energy consumption of the floor radiation and ventilation composite cooling system as a target function and taking the indoor comfort index PMV threshold range as a constraint condition;
and the cold supply system control module is used for determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
As a possible implementation manner of this embodiment, the PMV value prediction module is specifically configured to predict the PMV value by using an indoor environment dynamic heat and humidity modelTemperature of dry bulbt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises an indoor environment dynamic heat model and an indoor environment dynamic humidity model;
the indoor environment dynamic thermal model comprises the following steps:
Figure 188509DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,C i is the heat capacity of the air node, J/K;T i is the air node temperature, K;Q surf,i gain of radiant and convective heat on the surface of the enclosure, W;Q env,i w is the heat transferred to the air node through the wall;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain (generated by personnel, equipment, lighting, etc.), W;Q solar,i is the solar radiant heat gain through the window, W;Q r,i providing cold energy, W, for the floor radiation system to the air node;Q v,i the cooling capacity, W, provided to the air nodes by the ventilation system.
The indoor environment dynamic wet model is as follows:
Figure 781164DEST_PATH_IMAGE007
in the formula (I), the compound is shown in the specification,M eff,i the effective moisture capacity of the air node is g/g;ω i is the air node moisture content, g;W inf,i moisture gain due to permeated air, g;W int,i gain in indoor moisture content, g;W env to transfer the moisture content through the wall to the air nodes,g； W v,i the moisture removed for the vent system, g.
Before the working start time of personnel, the gains of indoor heat and moisture are approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
As a possible implementation manner of this embodiment, the objective optimization function is:
Figure 331094DEST_PATH_IMAGE008
Figure 274780DEST_PATH_IMAGE009
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump, kWh;ρ sw for the water density, kg/m 3 ；gIs the acceleration of gravity, m/s 2 ；HM is the lift of the circulating water pump;V sw for volume flow of water supply, m 3 /h；η pump The efficiency of the circulating water pump;E fan kWh is the fan energy consumption;DPis the fan pressure drop, pa;ρ a is the blast density in kg/m 3 ；V sa For volume flow of air supply, m 3 /s；η fan The fan efficiency; T out outdoor air temperature, deg.C;T set set point temperature, ° C;T out,dew the dew point temperature of outdoor air, C; dh v Is the enthalpy of evaporation, J/kg;ω out the moisture content of outdoor air is g/kg;ω max is the maximum moisture content set point, g/kg.
The constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
Referring to fig. 3 and 4, the following describes a specific process of the PMV index-based radiant cooling control of a buried pipe direct-supply floor according to the present invention, in combination with specific examples.
(1) Collecting indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values, and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate, and average radiant temperature.
The specific process of the step (1) comprises the following steps:
regularly collecting indoor environmental parameters including floor surface temperature and dry bulb temperaturet a Relative humidity ofRHAir flow ratev a Average radiation temperaturet r Air flow rate in generalv a The variation is small and is approximately considered as a constant value, and the thermal resistance of the clothes is setI cl Strength of movement of personsM0.5clo (summer) and 134W/person, respectively, then PMV values were automatically calculated:
Figure 319090DEST_PATH_IMAGE001
in the formula (I), the compound is shown in the specification,t a dry ball temperature, ° C;RHrelative humidity,%;v a is the air flow rate, m/s;t r mean radiation temperature, ° C;I cl is the garment thermal resistance, clo;Mhuman activity intensity, W; w is the mechanical work done by the human body, and is zero when sitting still, J;P a the partial pressure of water vapor of air around a human body is Pa;f cl is the dressing area coefficient;t cl to the outside of a garmentThe face temperature, ° C;h c is the convective heat transfer coefficient, W/(m) 2 ∙K)。
Figure 31831DEST_PATH_IMAGE002
Figure 487083DEST_PATH_IMAGE003
Figure 918065DEST_PATH_IMAGE004
Figure 15334DEST_PATH_IMAGE005
(2) Predicting a PMV value by adopting an indoor environment dynamic heat and humidity model;
the specific process of the step (2) comprises the following steps:
predicting the dry-bulb temperature by utilizing an indoor environment dynamic heat and humidity model according to the acquired real-time indoor environment parameterst a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personnelMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises the following components:
Figure 97428DEST_PATH_IMAGE012
in the formula (I), the compound is shown in the specification,C i is the heat capacity of the air node, J/K;T i is the air node temperature, K;Q surf,i gain of radiant and convective heat on the surface of the building envelope, W;Q env,i is the heat transferred to the air node through the wall, W;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain (generated by personnel, equipment, lighting, etc.), W;Q solar,i is the solar radiant heat gain through the window, W;Q r,i providing cold energy, W, for the floor radiation system to the air node;Q v,i the cooling capacity, W, provided to the air nodes by the ventilation system.
Figure 723581DEST_PATH_IMAGE007
In the formula (I), the compound is shown in the specification,M eff,i the effective moisture capacity of the air node is g/g;ω i is the air node moisture content, g;W inf,i moisture gain due to permeated air, g;W int,i gain for indoor moisture content, g;W env the moisture content g is transferred to the air node through the wall; W v,i the moisture removed for the vent system, g.
Before the working start time of personnel, the gain of indoor heat and moisture content is approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture content needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
(3) The lowest energy consumption of the floor radiation and ventilation composite cooling system is taken as an objective function, and the range of indoor comfort level index PMV threshold value [ -0.5, 0.5] is taken as a constraint condition.
The specific process of the step (3) comprises the following steps:
(3-1) establishing an objective optimization function as follows:
Figure 376280DEST_PATH_IMAGE013
Figure 277240DEST_PATH_IMAGE014
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump, kWh;ρ sw for the water density, kg/m 3 ；gIs the acceleration of gravity, m/s 2 ；HM is the lift of the circulating water pump;V sw for volume flow of water supply, m 3 /h；η pump The efficiency of the circulating water pump;E fan kWh is the fan energy consumption;DPis the fan pressure drop, pa;ρ a is the blast density in kg/m 3 ；V sa For volume flow of air supply, m 3 /s；η fan The fan efficiency; T out outdoor air temperature, deg.C;T set set point temperature, ° C;T out,dew the dew point temperature of outdoor air, C; dh v Is the evaporation enthalpy, J/kg;ω out the moisture content of outdoor air is g/kg;ω max is the maximum moisture content set point, g/kg.
(3-2) setting the constraint conditions as follows: through the process of starting precooling by a floor radiation and ventilation composite cooling system, PMV is required to be more than or equal to-0.5 and less than or equal to 0.5 at the time of starting personnel work; the PMV value calculated every 10 minutes is required to fall under-0.5, 0.5 during the staff hours.
The working time period of the staff is 9 to 00. The floor radiation system and ventilation system off time was fixed at 17.
(4) Determining the opening time of the ventilation system and the floor radiation system according to the moisture content to be removed indoors and the size relation between the surface temperature and the dew point temperature of the floor, and adjusting the sensible heat load bearing proportion S of the ventilation system and the floor radiation system according to the interval of the PMV value v /S R And controlling indoor thermal comfort index PMV.
The specific process of the step (4) comprises the following steps:
(4-1) calculating the pre-dehumidification time required by the ventilation system according to the moisture content to be removed indoors, the design air supply temperature and the design air supply quantity of the ventilation system, and determining the opening time of the ventilation system:
Figure 433414DEST_PATH_IMAGE010
in the formula (I), the compound is shown in the specification,tpre-dehumidification time h required by a ventilation system;V sa for volume flow of air supply, m 3 /h；WThe moisture content, g, to be removed indoors;d in is the moisture content of indoor air, g/kg;d sa is the air supply moisture content, g/kg.
And (4-2) when the temperature of the surface of the floor is higher than the dew point temperature, the floor radiation system is started.
(4-3) before the personnel working time, adjusting S according to the interval of the PMV value corresponding to the predicted personnel working starting time v /S R And determining the optimal water supply flow, air supply temperature and air supply quantity which meet the PMV threshold requirement and have the lowest energy consumption. After 10 minutes, collecting indoor parameters, predicting the indoor parameters corresponding to the working start time of the personnel, and adjusting S according to the interval of the PMV value obtained by calculation v /S R And determining the optimal operation parameters. If the working start time PMV of the personnel is less than or equal to 0.5, the water supply flow of the floor radiation system is adjusted to a design value, and the air supply volume and the air supply temperature of the ventilation system are adjusted to the design value; if the staff starts working PMV>0.5, increase S v /S R And adjusting the water supply flow of the floor radiation system to be the maximum value based on the objective function and the constraint condition, adjusting the air supply quantity and the air supply temperature by the ventilation system based on the minimum adjustment amplitude, and determining the optimal value.
S v /S R Can be expressed as:
Figure 512360DEST_PATH_IMAGE011
in the formula (I), the compound is shown in the specification,Q vent. for replacement of ventilation systemsSensible heat load, kW ∙ h;Q RFC the sensible heat load borne by a floor radiation system is kW ∙ h;T in indoor air temperature, ° C;T sa the temperature of the air supply is equal to DEG C;Ais the floor surface area, m 2 ；h t W/(m) is the overall heat transfer coefficient 2 ∙K)；T op Operating temperature, ° C;T f the surface temperature of the floor is ° C.
(4-4) adjusting S according to the interval of the PMV value after 10 minutes predicted at the present moment in the staff working period v /S R And determining the optimal air supply temperature and air supply quantity which meet the PMV threshold requirement and have the lowest energy consumption. After 10 minutes interval, indoor parameters were collected and the dry bulb temperature after 10 minutes was predictedt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMAdjusting S according to the calculated interval of PMV value v /S R And determining the optimal operation parameters. If the PMV after 10 minutes is less than or equal to 0.5, adjusting the air output of the ventilation system to be the minimum fresh air quantity, and adjusting the air supply temperature to be a design value; PMV after 10 minutes>0.5, increase S v /S R And based on the objective function and the constraint condition, the ventilation system adjusts the air supply quantity and the air supply temperature based on the minimum adjustment amplitude, and determines an optimal value.
At the moment of starting staff work, setting the initial operating parameters of the ventilation system: designing air supply temperature and air supply volume, setting initial operation parameters of a floor radiation system: if the surface temperature of the floor does not meet the design requirement, the floor radiation cooling system operates at the maximum allowable water supply flow and is kept unchanged; if the surface temperature of the floor reaches the design requirement, the floor radiation cooling system operates at the designed water supply flow and is kept unchanged.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting the same, and although the present invention is described in detail with reference to the above embodiments, those of ordinary skill in the art should understand that: modifications and equivalents may be made to the embodiments of the invention without departing from the spirit and scope of the invention, which is to be covered by the claims.

Claims (10)

1. A PMV-based buried pipe direct supply floor radiation cooling control method is characterized by comprising the following steps:
collecting indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values, and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature;
predicting a PMV value by adopting an indoor environment dynamic heat and humidity model;
setting a control rule for the operation of a cooling system by taking the lowest energy consumption of a floor radiation and ventilation composite cooling system as a target function and taking an indoor comfort index PMV threshold range as a constraint condition;
and determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
2. The PMV-based buried pipe direct supply floor radiant cooling control method of claim 1, wherein the predicting PMV value by using the indoor environment dynamic thermo-hygro model comprises:
predicting dry bulb temperature by utilizing indoor environment dynamic heat and humidity modelt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises the following components:
Figure 149960DEST_PATH_IMAGE001
in the formula (I), the compound is shown in the specification,C i the thermal capacity of the air node;T i is the air node temperature;Q surf,i gain radiation and convection heat for the surface of the building envelope;Q env,i the heat is transferred to the air node through the wall;Q inf,i heat gain due to permeated air;Q int,i indoor convection and radiant heat gains;Q solar,i is the solar radiant heat gain through the window;Q r,i providing cold energy for the floor radiation system to the air node;Q v,i providing cold energy for the ventilation system to the air node;
Figure 598259DEST_PATH_IMAGE002
in the formula (I), the compound is shown in the specification,M eff,i effective moisture capacity for air nodes;ω i is the air node moisture content;W inf,i moisture content gain for permeated air;W int,i gain for indoor moisture content;W env the moisture content is transferred to the air node through the wall body; W v,i moisture removed for the ventilation system;
before the working start time of personnel, the gain of indoor heat and moisture content is approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture content needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
3. The PMV-based buried pipe direct supply floor radiant cooling control method according to claim 1, wherein the objective optimization function is:
Figure 643575DEST_PATH_IMAGE003
Figure 569943DEST_PATH_IMAGE004
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump is reduced;ρ sw is the density of the water supply;gis the acceleration of gravity;Hthe water circulation pump lift is adopted;V sw is the volume flow of water supply;η pump the efficiency of the circulating water pump;E fan the energy consumption of the fan is reduced;DPis the fan pressure drop;ρ a is the blowing density;V sa is the volume flow of the air supply;η fan the fan efficiency; T out is the outdoor air temperature;T set is a set point temperature;T out,dew is the outdoor air dew point temperature; dh v Is the enthalpy of evaporation, J/kg;ω out is the outdoor air moisture content;ω max is the maximum moisture content set point;
the constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
4. The PMV-based buried pipe direct supply floor radiant cooling control method of claim 1, wherein the determining the opening time of the ventilation system and the floor radiant system and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing ratio of the ventilation system and the floor radiant system according to the interval of the PMV value comprises:
according to the moisture content to be removed indoors and the design air supply temperature and the design air supply quantity of the ventilation system, calculating the pre-dehumidification time required by the ventilation system, and determining the starting time of the ventilation system:
Figure 666206DEST_PATH_IMAGE005
in the formula (I), the compound is shown in the specification,tpre-dehumidification time required for a ventilation system;V sa is the volume flow of the air supply;Wthe moisture content to be removed in the room;d in is the indoor air moisture content;d sa the moisture content of the air supply;
when the surface temperature of the floor is higher than the dew point temperature, the floor radiation system is started;
before the working time of the personnel, according to the predicted interval of PMV value corresponding to the working starting time of the personnel, the sensible heat load bearing proportion S of the ventilation system and the floor radiation system is adjusted v /S R Determining the optimal water supply flow, air supply temperature and air supply quantity which meet the PMV threshold requirement and have the lowest energy consumption;
during the working time of the personnel, S is adjusted according to the predicted PMV value interval after 10 minutes at the current moment v /S R And determining the optimal air supply temperature and air supply quantity.
5. The PMV-based buried pipe direct supply floor radiant cooling control method according to claim 1, wherein the personnel working time period is 9 to 00; the floor radiation system and ventilation system off time was 17.
6. The PMV-based direct geothermal piping cooling by radiation on floor control method according to claim 1, wherein the sensible heat load bearing ratio S of the ventilation system to the radiant flooring system is adjusted v /S R Expressed as:
Figure 754248DEST_PATH_IMAGE006
in the formula (I), the compound is shown in the specification,Q vent. sensible heat load to the displacement ventilation system;Q RFC sensible heat load borne for the floor radiant system;T in is the indoor air temperature;T sa is the temperature of the air supply;Ais the floor surface area;h t is the overall heat transfer coefficient;T op is the operating temperature;T f is the floor surface temperature.
7. The PMV-based direct underfloor radiant cooling control method according to any one of claims 1 to 6, wherein the determining of the optimum supply air temperature and the supply air volume comprises:
at the moment of starting staff work, setting the initial operating parameters of the ventilation system: designing air supply temperature and air supply quantity, and setting initial operation parameters of a floor radiation system;
if the surface temperature of the floor does not meet the design requirement, the floor radiation cooling system operates at the maximum allowable water supply flow and is kept unchanged;
if the surface temperature of the floor reaches the design requirement, the floor radiation cooling system operates at the designed water supply flow and is maintained unchanged.
8. A PMV-based buried pipe direct supply floor radiation cooling control device is characterized by comprising:
the data acquisition processing module is used for acquiring indoor environment parameters, setting the thermal resistance of clothes and the activity intensity of personnel as fixed values and calculating a PMV value; the indoor environmental parameters include floor surface temperature, dry bulb temperature, relative humidity, air flow rate and average radiation temperature;
the PMV value prediction module is used for predicting the PMV value by adopting an indoor environment dynamic heat and humidity model;
the control rule setting module is used for setting a control rule for the operation of the cooling system by taking the lowest energy consumption of the floor radiation and ventilation composite cooling system as a target function and taking the indoor comfort index PMV threshold range as a constraint condition;
and the cold supply system control module is used for determining the starting time of the ventilation system and the floor radiation system, and controlling the indoor thermal comfort index PMV by adjusting the sensible heat load bearing proportion of the ventilation system and the floor radiation system according to the interval of the PMV value.
9. The PMV-based buried pipe direct supply floor radiant cooling control device of claim 8, wherein the PMV value prediction module is specifically configured to predict dry bulb temperature using an indoor environment dynamic thermo-wet modelt a Relative humidity ofRHAverage radiation temperaturet r In combination with the determined air flow ratev a Thermal resistance of clothesI cl Strength of movement of personsMCalculating a PMV value;
the indoor environment dynamic heat and humidity model comprises an indoor environment dynamic heat model and an indoor environment dynamic humidity model;
the indoor environment dynamic thermal model comprises the following steps:
Figure 552439DEST_PATH_IMAGE001
in the formula (I), the compound is shown in the specification,C i the thermal capacity of the air node;T i is the air node temperature;Q surf,i gain radiation and convection heat for the surface of the building envelope;Q env,i the heat is transferred to the air node through the wall;Q inf,i for the thermal gain due to the infiltration of air, W;Q int,i indoor convection and radiant heat gain;Q solar,i is the solar radiant heat gain through the window;Q r,i cold energy provided for the floor radiation system to the air nodes;Q v,i providing cold energy for the ventilation system to the air node;
the indoor environment dynamic wet model is as follows:
Figure 16919DEST_PATH_IMAGE002
in the formula (I), the compound is shown in the specification,M eff,i effective moisture capacity for air nodes;ω i is the air node moisture content;W inf,i moisture content gain for permeated air;W int,i gain for indoor moisture content;W env the moisture content is transferred to the air node through the wall body; W v,i moisture removed for the ventilation system;
before the working start time of personnel, the gain of indoor heat and moisture content is approximately zero, and the heat and moisture transfer from outdoor to indoor is less, so that only the residual heat and moisture content needing to be removed are considered and substituted into the formula for solving; in the working time period of personnel, the indoor heat source time schedule is determined, and outdoor weather is smaller than the influence of the indoor heat source on the indoor heat environment, and the outdoor weather parameter changes less within 10 minutes of the collection interval and is approximately considered to be constant, so that the currently collected outdoor weather parameter value is adopted and substituted into the formula for solving.
10. The PMV-based buried pipe direct supply floor radiant cooling control device of claim 8, wherein the objective optimization function is:
Figure 216956DEST_PATH_IMAGE003
Figure 475899DEST_PATH_IMAGE007
in the formula (I), the compound is shown in the specification,E pump energy consumption of a circulating water pump is reduced;ρ sw is the density of the water supply;gis the acceleration of gravity;Hthe water circulation pump lift is adopted;V sw for supplying waterThe volume flow rate;η pump the efficiency of the circulating water pump;E fan the energy consumption of the fan is reduced;DPis the fan pressure drop;ρ a is the blowing density;V sa is the volume flow of the air supply;η fan the fan efficiency; T out is the outdoor air temperature;T set is a set point temperature;T out,dew is the outdoor air dew point temperature; dh v Is the enthalpy of vaporization;ω out is the outdoor air moisture content;ω max is the maximum moisture content set point;
the constraint conditions are as follows: starting a pre-cooling process through a floor radiation and ventilation combined cooling system, and requiring a PMV value to fall within a PMV threshold range at the working start time of personnel; the PMV values calculated every 10 minutes required during the crew work period fall within the PMV threshold range.
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CN116931629A (en) * 2023-09-18 2023-10-24 湖南朗赫科技有限公司 Control method, system and storage medium for preventing indoor moisture regain and dew condensation
CN117232084A (en) * 2023-11-13 2023-12-15 山东建筑大学 Control method and device of radiation type air conditioning system based on man-machine interaction
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WO2024090465A1 (en) * 2022-10-27 2024-05-02 パナソニックＩｐマネジメント株式会社 Radiant air conditioning system
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CN117663390A (en) * 2023-12-04 2024-03-08 深圳市亚晔实业有限公司 Fresh air control system and method based on Internet of things
CN117663390B (en) * 2023-12-04 2024-10-22 深圳市亚晔实业有限公司 Fresh air control system and method based on Internet of things

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