CN115143558A - Temperature and humidity independent control air conditioner demand response control method and refrigeration system - Google Patents
Temperature and humidity independent control air conditioner demand response control method and refrigeration system Download PDFInfo
- Publication number
- CN115143558A CN115143558A CN202210795343.6A CN202210795343A CN115143558A CN 115143558 A CN115143558 A CN 115143558A CN 202210795343 A CN202210795343 A CN 202210795343A CN 115143558 A CN115143558 A CN 115143558A
- Authority
- CN
- China
- Prior art keywords
- cold
- cold storage
- water tank
- temperature
- demand response
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000004044 response Effects 0.000 title claims abstract description 121
- 238000000034 method Methods 0.000 title claims abstract description 25
- 238000005057 refrigeration Methods 0.000 title abstract description 14
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 412
- 238000004378 air conditioning Methods 0.000 claims abstract description 16
- 238000009825 accumulation Methods 0.000 claims description 87
- 238000001816 cooling Methods 0.000 claims description 25
- 230000005855 radiation Effects 0.000 claims description 22
- 238000013486 operation strategy Methods 0.000 claims description 12
- 238000013461 design Methods 0.000 claims description 6
- 239000012530 fluid Substances 0.000 claims description 6
- 239000007788 liquid Substances 0.000 claims description 6
- 238000004321 preservation Methods 0.000 claims description 3
- 238000005265 energy consumption Methods 0.000 abstract description 2
- 230000005494 condensation Effects 0.000 description 4
- 238000009833 condensation Methods 0.000 description 4
- 238000011217 control strategy Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000012549 training Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 238000010977 unit operation Methods 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Images
Classifications
-
- 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
- F24F5/0017—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 using cold storage bodies, e.g. ice
-
- 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
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/46—Improving electric energy efficiency or saving
-
- 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
-
- 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
- F24F11/80—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
- F24F11/84—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 using valves
-
- 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
- F24F11/85—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 using variable-flow pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
-
- 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
- F24F5/0003—Exclusively-fluid systems
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Signal Processing (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention provides a demand response control method for an air conditioner capable of independently controlling temperature and humidity and a refrigeration system, and belongs to the field of operation regulation and control of air conditioning systems. According to the demand response control method for the air conditioner and the refrigerating system with the independent temperature and humidity control function, on the basis of effectively reducing the cold storage amount by combining the advantages of the independent temperature and humidity control air conditioner system and the water cold storage system, the cold storage and the cold release of the cold storage water tank are effectively scheduled, and on the premise that the thermal comfort is within the acceptable range of indoor personnel, the operation scheme of the air conditioner system in the demand response period is flexibly selected according to the relation between the actual maximum cold storage amount and the theoretical cold storage amount of the cold storage water tank. Compared with the prior art, the method ensures the flexibility and better controllability of energy, fully utilizes the demand response potential of the chilled water storage system, can reduce the peak load of electric power, improves the current supply and demand situation of a power grid, and reduces the operation energy consumption of the air conditioning system.
Description
Technical Field
The invention relates to the field of operation regulation and control of air conditioning systems, in particular to a demand response control method for an air conditioner capable of independently controlling temperature and humidity and a refrigeration system.
Background
With the rapid development of socio-economy and the transformation and upgrading of energy structures, the demand of society for electricity continues to rapidly increase and shows a significant peak-to-valley difference due to human activities, thereby posing a serious challenge to the reliability of power supply. At present, the load characteristics of the power grid in the summer peak power utilization period of China continuously deteriorate, the power utilization shortage phenomenon frequently appears, although the power utilization shortage phenomenon can be relieved by building a peak regulation power plant and expanding installed capacity, the peak load is not reduced, the construction cost of the power grid is undoubtedly increased, and the sustainable development of the intelligent power grid is not facilitated.
Meanwhile, with global warming, high-temperature weather in summer increases, and extremely high temperature day continuously appears, so that the proportion of temperature control loads of air conditioners and the like is increased year by year, and the load ratio of the air conditioner loads in most areas of China in the peak period of power utilization is nearly half. Considering that the air conditioning load is taken as a flexible temperature control load, the flexible temperature control load has the characteristic of quick response to short-time regulation and control, and is a demand response resource with great potential. Therefore, a reasonable control strategy of the air conditioning system is researched and formulated to participate in the response of the demand side, and the method has important significance for improving the current supply and demand situation of the power grid, reducing the peak load and reducing the construction cost of the power grid. The cold storage air conditioning technology is used as an important content of electric power demand side management, better controllability can be kept while energy flexibility is ensured, but the conventional chilled water storage air conditioner has the defects that the cold storage amount is larger due to heat and humidity combined treatment, and the economical efficiency and the practicability are influenced. In addition, aiming at the conventional chilled water storage air conditioning system project in the actual operation at present, a cold machine and a cold storage device are generally connected in series, but the phenomenon of poor operation effect is easy to occur in consideration of the influence of various factors such as the technical experience of workers, the setting of system parameters, the operation of a control strategy and the like in the actual process. For example, when a certain chilled water storage air conditioning system adopts a serial connection form of a cold machine and a cold storage device and adopts a preferential cold release strategy of the cold storage device, the situation that the cold storage amount of the cold storage device cannot meet the requirement easily occurs in certain extremely severe weather, and if the cold release strategy is not reasonably optimized according to the load change characteristic in the situation, the situation that the cold machine still needs to be started for cold supply during the peak period of the electric load is further caused, and meanwhile, the situation that the indoor thermal comfort cannot be controlled and further deviates from the normal range in a short time due to the sudden nature of an event may occur.
Considering that the temperature and humidity independent control air conditioning system is respectively used for processing and adjusting the temperature and the humidity by the independent subsystems, if only the sensible heat cold load is stored, compared with the conventional chilled water storage air conditioner which needs to store the total cold load, the chilled water storage quantity can be obviously reduced. Therefore, the temperature and humidity independent control air conditioning system and the chilled water storage system are combined, and a proper control strategy is formulated, so that the problems of the conventional chilled water storage air conditioner can be avoided, the demand response potential of the chilled water storage system can be fully utilized, and the pressure of the power load in the peak period is reduced.
Disclosure of Invention
In order to solve the problems, the invention discloses a demand response control method of an air conditioner capable of independently controlling temperature and humidity and a refrigeration system.
The invention is realized by the following technical scheme:
a demand response control method and a refrigeration system for an independent temperature and humidity control air conditioner are applied to the independent temperature and humidity control air conditioner system, and the independent temperature and humidity control air conditioner system comprises a controller, a humidity control subsystem and a temperature control subsystem; the humidity control subsystem comprises a water chilling unit, a circulating water pump and a dehumidifying fresh air unit; the temperature control subsystem comprises a high-temperature water chilling unit, a circulating water pump, a cold accumulation water tank and an indoor heat exchange tail end, wherein the high-temperature water chilling unit is respectively connected with the indoor heat exchange tail end and the cold accumulation water tank through water supply branch pipes;
the method comprises the following steps:
step one, forecasting hourly cooling load born by a temperature control subsystem on the next day by using a support vector regression model;
secondly, determining the theoretical cold accumulation amount of the cold accumulation water tank according to the predetermined demand response time period and the predicted hourly cold load borne by the temperature control subsystem;
checking theoretical cold storage amount and actual maximum cold storage amount of the cold storage water tank, evaluating feasibility of various operation schemes, and further determining an optimal operation scheme of a demand response period;
the steps for determining the optimal operation scheme in the demand response period are as follows:
if the actual maximum cold accumulation amount of the cold accumulation water tank can meet the theoretical cold accumulation amount, a scheme A is adopted for the operation strategy in the response time interval; if the actual maximum cold accumulation amount of the cold accumulation water tank is close to but cannot meet the theoretical cold accumulation amount, calculating the cold release time of the cold accumulation water tank, determining the advanced startup time of the high-temperature water chilling unit, and adopting a scheme B for a demand response time interval operation strategy; if the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount and the starting time of the high-temperature water chilling unit is too long in advance, a scheme C is adopted for the operation strategy in the demand response period; if the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount and the possibility that the requirement of the demand response time period cannot be met is still considered in the case of adopting the scheme C under the extremely severe weather condition, adopting a scheme D by the operation strategy of the demand response time period;
the scheme is as follows:
scheme A: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold energy is the theoretical cold storage amount of the cold storage water tank, and the cold energy required by the temperature control subsystem is provided through the cold storage water tank in the response time period;
scheme B: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the difference value of the cold release time length, the demand response time period and the energy release time length is calculated, the advanced starting time of the high-temperature water chiller is determined, and the cold quantity required by the temperature control subsystem is provided by the cold storage water tank and the high-temperature water chiller in sequence in the demand response time period;
scheme C: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the indoor set temperature in the demand response time period is increased based on the acceptable range of indoor thermal comfort, the requirement of the demand response time period can be met until the cold release time of the cold storage water tank at the current indoor set temperature is long, and the cold quantity required by the temperature control subsystem is provided through the cold storage water tank in the demand response time period;
scheme D: under extremely severe weather conditions, considering the possibility that the requirement of the demand response time interval cannot be met after the scheme C is adopted and considering the non-occupied time interval, carrying out cold accumulation on the cold accumulation water tank through the high-temperature water chiller, wherein the stored cold amount is the actual maximum cold accumulation amount of the cold accumulation water tank, taking the highest temperature as the indoor set temperature of the demand response time interval within the indoor thermal comfort acceptable range, calculating the cold release time length, the difference value between the demand response time interval and the cold release time length, and determining the advanced starting time of the high-temperature water chiller, wherein the cold accumulation water tank and the high-temperature water chiller successively provide the cold amount required by the temperature control subsystem in the demand response time interval;
optionally, the collecting of the relevant parameters in the first step includes using historical hourly cooling load born by the temperature control subsystem, outdoor meteorological parameters and indoor personnel and equipment work and rest as input parameters, and predicting the hourly cooling load born by the temperature control subsystem on the next day through a support vector regression model.
Optionally, the theoretical cold storage amount of the cold storage water tank in the second step refers to a cold amount theoretically required to be borne by the temperature control subsystem in the demand response period, and a calculation formula is as follows:
in the formula: q i The theoretical cold accumulation amount of the cold accumulation water tank is shown; q CL (t) the predicted next day hourly cooling load;
t 1 is the starting time of the demand response period; t is t 2 Is the end time of the demand response period;
optionally, in the third step, the actual maximum cold storage amount of the cold storage water tank is limited by the effective volume of the cold storage water tank and the design condition of the temperature control subsystem, and the theoretical cold storage amount and the actual maximum cold storage amount of the cold storage water tank need to be checked under the condition that the requirement of the theoretical cold storage amount cannot be met.
Optionally, in the third step, the actual maximum cold storage amount of the cold storage water tank is calculated according to the following formula:
Q a ＝C p ρVΔT a η 1
in the formula: q a The actual maximum cold storage capacity of the cold storage water tank; c p The specific heat capacity of the cold storage liquid in the cold storage water tank; rho is the density of the liquid in the cold storage water tank; v is the effective volume of the cold accumulation water tank; delta T a The temperature difference of fluid at the inlet and the outlet of the cold accumulation water tank under the design working condition is designed; eta 1 The heat preservation efficiency of the cold storage water tank is improved; optionally, in the third step, a cold release duration calculation formula of the cold storage water tank is as follows:
t d ＝(V/v)×(ΔT a /ΔT d )
in the formula: t is t d The time for releasing cold of the cold storage water tank; v is the effective volume of the cold accumulation water tank; v is the volume flow of the chilled water when the cold storage water tank releases cold in the demand response period; delta Ta is the temperature difference of the fluid at the inlet and the outlet of the cold accumulation water tank under the design working condition; delta Td is the indoor heat exchange end of the temperature control subsystemTemperature difference of supply and return water;
the refrigeration system of the control method comprises a controller, a humidity control subsystem and a temperature control subsystem; the humidity control subsystem comprises a water chilling unit, a circulating water pump and a dehumidifying fresh air unit; the temperature control subsystem comprises a high-temperature water chilling unit, a circulating water pump, a cold accumulation water tank and an indoor heat exchange tail end, wherein the high-temperature water chilling unit is respectively connected with the indoor heat exchange tail end and the cold accumulation water tank through water supply branch pipes; the water supply and return branch pipes are respectively provided with an electromagnetic valve, and the electromagnetic valves receive control signals from the controller and are used for controlling the on-off of the water channel.
Optionally, the indoor heat exchange end is a radiation ceiling or a dry type fan coil.
Optionally, chilled water provided by a water chilling unit in the humidity control subsystem is delivered to a dehumidification fresh air unit by a circulating water pump, the dehumidification fresh air unit is used for refrigerating and dehumidifying fresh air, and the fresh air is delivered indoors by a power device to bear all latent heat cold load and part sensible heat cold load indoors; chilled water provided by a high-temperature water chilling unit in the temperature control subsystem is respectively sent to the indoor heat exchange tail end and the cold accumulation water tank by the circulating water pump based on control signals of the controller at different time intervals, and most of indoor sensible heat cold load is borne.
Compared with the prior art, the invention has the following beneficial technical effects:
according to the demand response control method and the refrigeration system for the air conditioner with the independent temperature and humidity control function, on the basis of effectively reducing the cold storage amount by combining the advantages of the independent temperature and humidity control system and the water cold storage system, the cold storage and the cold release of the cold storage water tank are effectively scheduled, and on the premise that the thermal comfort is within the acceptable range of indoor personnel, the operation scheme of the air conditioner system with the demand response time period is flexibly selected according to the relation between the actual maximum cold storage amount and the theoretical cold storage amount of the cold storage water tank, so that the flexibility and the good controllability of energy are ensured, the demand response potential of the water cold storage system is fully utilized, the peak load of electric power can be reduced, the supply and demand current situation of a power grid is improved, and the operation energy consumption of the air conditioner system is reduced.
Drawings
FIG. 1 is a flow chart of an embodiment of the method of the present invention;
FIG. 2 is a schematic diagram of a refrigeration system according to the present invention;
list of reference numerals:
1. a controller; 2. a water chilling unit; 3. a dehumidifying fresh air handling unit; 4. a high temperature water chilling unit; 5. a cold storage water tank; 6. an indoor heat exchange end; 7. a first solenoid valve; 8. a second solenoid valve; 9. a third electromagnetic valve; 10. a fourth solenoid valve; 11. a first circulating water pump; 12. a second circulating water pump; 13. and a third circulating water pump.
Detailed Description
The present invention will be further illustrated with reference to the accompanying drawings and specific embodiments, which are to be understood as merely illustrative of the invention and not as limiting the scope of the invention.
As shown in fig. 1, the present embodiment provides a demand response control method for an air conditioner with independent temperature and humidity control, where the control method includes the following steps:
step one, forecasting hourly cooling load born by a temperature control subsystem on the next day by using a support vector regression model;
and predicting the hourly cooling load born by the temperature control subsystem the next day by using a support vector regression model, and acquiring related parameters including historical hourly cooling load born by the temperature control subsystem, outdoor air dry bulb temperature, outdoor air relative humidity, solar radiation intensity and indoor personnel equipment work and rest as input parameters.
Secondly, determining the theoretical cold accumulation amount of the cold accumulation water tank according to the predetermined demand response time period and the predicted hourly cold load borne by the temperature control subsystem;
the determination of the demand response time interval needs to take various factors into consideration, such as the power load peak time intervals of power grids in different regions and the market power prices in different regions, including the real-time power price, the time-of-use power price and the peak power price;
the theoretical cold accumulation amount of the cold accumulation water tank refers to the cold amount theoretically needed to be born by the temperature control subsystem in the demand response period;
the theoretical cold accumulation amount calculation formula of the cold accumulation water tank is as follows:
in the formula: q i The theoretical cold accumulation amount of the cold accumulation water tank is shown; q CL (t) the predicted next day hourly cooling load;
t 1 is the starting time of the demand response period; t is t 2 The end time of the demand response period.
Checking the theoretical cold accumulation amount and the actual maximum cold accumulation amount of the cold accumulation water tank, evaluating the feasibility of various operation schemes, and further determining the optimal operation scheme in the demand response period;
the actual maximum cold accumulation amount of the cold accumulation water tank cannot meet the requirement of theoretical cold accumulation amount possibly due to the limitation of the volume of the cold accumulation water tank and the operation condition of the temperature control subsystem, so that the theoretical cold accumulation amount and the actual maximum cold accumulation amount of the cold accumulation water tank need to be checked, and the optimal operation scheme of a demand response period is determined according to the theoretical cold accumulation amount and the actual maximum cold accumulation amount of the cold accumulation water tank;
the steps for determining the optimal operation scheme in the demand response period are as follows:
if the actual maximum cold storage amount of the cold storage water tank can meet the theoretical cold storage amount, a scheme A is adopted for the operation strategy in the response time period; if the actual maximum cold storage amount of the cold storage water tank is close to but cannot meet the theoretical cold storage amount, calculating the cold release time of the cold storage water tank, determining the advanced starting time of the high-temperature water chilling unit, and adopting a scheme B in a demand response time interval operation strategy; if the actual maximum cold accumulation of the cold accumulation water tank cannot meet the theoretical cold accumulation and the time for starting the high-temperature water chilling unit in advance is too long, the demand response time interval operation strategy adopts a scheme C; if the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount and the possibility that the requirement of the demand response time period cannot be met is still considered in the case of adopting the scheme C under the extremely severe weather condition, adopting a scheme D by the operation strategy of the demand response time period;
through the steps, the operation scheme of the demand response time interval is reasonably selected according to different conditions, and the starting time of the high-temperature water chilling unit in the demand response time interval is reduced as much as possible, so that the demand response potential of the chilled water storage system is fully exerted.
The above schemes are as follows:
scheme A: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold energy is the theoretical cold storage amount of the cold storage water tank, in the response time period, the electromagnetic valve of the water supply and return passage between the high-temperature water chiller and the indoor heat exchange tail end is closed, the electromagnetic valve of the water supply and return passage between the cold storage water tank and the indoor heat exchange tail end is opened, and the cold energy required by the temperature control subsystem is provided through the cold storage water tank;
scheme B: in a non-occupied period, cold storage is carried out on the cold storage water tank through the high-temperature water chiller, the stored cold energy is the actual maximum cold storage amount of the cold storage water tank, the energy release duration and the difference value between the demand response period and the energy release duration are calculated, the starting-up time of the high-temperature water chiller is determined, the electromagnetic valve on a water supply and return passage between the cold storage water tank and the indoor heat exchange tail end is closed at the time point, the electromagnetic valve on the water supply and return passage between the high-temperature water chiller and the indoor heat exchange tail end is opened, the high-temperature water chiller provides the cold energy needed by the temperature control subsystem, and the cold storage water tank and the high-temperature water chiller provide the cold energy needed by the temperature control subsystem in the demand response period;
scheme C: in the non-occupied period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the indoor set temperature in the demand response period is increased based on the acceptable range of the indoor comfort level, the requirement of the demand response period can be met until the energy release time of the cold storage water tank at the current indoor set temperature is long, the electromagnetic valve of a water supply and return passage between the high-temperature water chiller and the indoor heat exchange tail end is closed in the demand response period, the electromagnetic valve of the water supply and return passage between the cold storage water tank and the indoor heat exchange tail end is opened, and the cold quantity required by the temperature control subsystem is provided through the cold storage water tank;
scheme D: under the extremely severe weather condition, considering the possibility that the requirement of the demand response time period cannot be met after the scheme C is adopted and considering the non-occupied time period, carrying out cold storage on the cold storage water tank through the high-temperature water chiller, wherein the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, taking the highest temperature as the indoor set temperature of the demand response time period within the acceptable range of indoor thermal comfort, calculating the difference value of the cold release time length, the demand response time length and the cold release time length, determining the advanced starting time of the high-temperature water chiller, closing an electromagnetic valve on a water supply and return passage between the cold storage water tank and the indoor heat exchange tail end at the time point, opening an electromagnetic valve of a water supply and return passage between the high-temperature water chiller and the indoor heat exchange tail end, providing the cold quantity required by the temperature control subsystem through the high-temperature water chiller, and providing the cold quantity required by the temperature control subsystem successively by the cold storage water tank and the high-temperature water chiller in the demand response time period;
the actual maximum cold accumulation amount calculation formula of the cold accumulation water tank is as follows:
Q a ＝C p ρVΔT a η 1
in the formula: q a The actual maximum cold storage capacity of the cold storage water tank; c p The specific heat capacity of the cold storage liquid in the cold storage water tank; rho is the density of the liquid in the cold storage water tank; v is the effective volume of the cold accumulation water tank; delta T a The temperature difference of the inlet and outlet fluid of the cold accumulation water tank is designed under the working condition; eta 1 The heat preservation efficiency of the cold accumulation water tank is improved.
The cold release time calculation formula of the cold storage water tank is as follows:
t d ＝(V/v)×(ΔT a /ΔT d )
in the formula: t is t d The time length of cold release of the cold storage water tank is; v is the effective volume of the cold accumulation water tank; v is the volume flow of the chilled water when the cold storage water tank releases cold in the demand response period; delta Ta is the temperature difference of the fluid at the inlet and the outlet of the cold accumulation water tank under the design working condition; and delta Td is the temperature difference of water supply and return at the indoor heat exchange end of the temperature control subsystem.
As shown in fig. 2, the present invention provides a refrigeration system using the above control method, which includes a controller 1, a humidity control subsystem, and a temperature control subsystem; the humidity control subsystem comprises a water chilling unit 2, a first circulating water pump 11 and a dehumidifying fresh air unit 3; the temperature control subsystem comprises a high-temperature water chilling unit 4, a second circulating water pump 12, a third circulating water pump 13, a cold accumulation water tank 5 and an indoor heat exchange tail end 6.
The water chilling unit 2 is connected with the dehumidifying fresh air unit 3 through a water supply pipe, the dehumidifying fresh air unit 3 is connected with the first circulating water pump 11 through a water return pipe, and finally, the chilled water flows back to the water chilling unit 2 to form the whole circulation of a water system of the humidity control subsystem; the dehumidifying fresh air unit 3 is connected with outdoor fresh air through a fresh air pipe and is connected with an indoor air supply end through an air supply pipe to form the whole circulation of an air system of the humidity control subsystem.
Chilled water provided by a water chilling unit 2 in a humidity control subsystem is delivered to a dehumidifying fresh air unit 3 by a first circulating water pump 11, the dehumidifying fresh air unit 3 refrigerates and dehumidifies fresh air, and the fresh air is delivered to the indoor space by a power device to bear all indoor latent heat cold loads and part indoor sensible heat cold loads.
The high-temperature water chilling unit 4 is connected with the indoor heat exchange tail end 6 through a water supply branch pipe, the indoor heat exchange tail end 6 is connected with the second circulating water pump 12 through a water return branch pipe, and finally high-temperature chilled water flows back to the high-temperature water chilling unit 4 to form a water loop for cooling of the temperature control subsystem; the high-temperature water chilling unit 4 is connected with the cold accumulation water tank 5 through a water supply branch pipe, the cold accumulation water tank 5 is connected with the second circulating water pump 12 through a water return branch pipe, and finally high-temperature chilled water flows back to the high-temperature water chilling unit 4 to form a water loop for cold accumulation of the temperature control subsystem; a water supply and return passage is additionally arranged between the cold accumulation water tank 5 and the indoor heat exchange tail end 6, the cold accumulation water tank 5 is connected with the indoor heat exchange tail end 6 through a water supply pipe, the indoor heat exchange tail end 6 is connected with a third circulating water pump 13 through a water return pipe, and finally high-temperature chilled water flows back to the cold accumulation water tank 5 to form a water loop for cooling the cold accumulation water tank of the temperature control subsystem; a second electromagnetic valve 8, a third electromagnetic valve 9 and a fourth electromagnetic valve 10 are respectively arranged on water supply pipes of the water loop for cold supply of the temperature control subsystem cold machine, the water loop for cold accumulation of the temperature control subsystem cold machine and the water loop for cold supply of the temperature control subsystem cold accumulation water tank; the second electromagnetic valve 8, the third electromagnetic valve 9 and the fourth electromagnetic valve 10 receive control signals from the controller 1 to control the on-off of the water path.
Wherein the indoor heat exchange tail end 6 is a radiation ceiling or a dry type fan coil.
The high-temperature chilled water provided by the high-temperature water chilling unit 4 in the temperature control subsystem is respectively sent to the indoor heat exchange tail end 6 and the cold accumulation water tank 5 by the second circulating water pump 12 based on the control signal of the controller 1 at different time intervals, and most of indoor sensible heat and cold load is borne.
For example, when the optimal operation scheme of the demand response time period is determined to be the scheme a according to the steps, the high-temperature water chilling unit 4 receives a control signal from the controller 1 in the non-occupied time period, and sends the high-temperature chilled water to the cold storage water tank 5 through the second circulating pump 12, wherein the stored cold amount is the theoretical cold storage amount of the cold storage water tank; the high-temperature water chilling unit 4 receives a control signal from the controller 1 at the initial time of the occupation time, sends high-temperature chilled water to the indoor heat exchange tail end 6 through the second circulating water pump 12, and bears most of indoor sensible heat cooling load from the initial time of the occupation time to the initial time of the demand response time period; the cold accumulation water tank 5 receives a control signal from the controller 1 at the initial moment of the demand response time period, and sends high-temperature chilled water to the indoor heat exchange tail end 6 through the third circulating water pump 13 to bear most of indoor sensible heat cold load in the demand response time period; the high-temperature water chilling unit 4 receives a control signal from the controller 1 at the end of the demand response time period, sends high-temperature chilled water to the indoor heat exchange tail end 6 through the second circulating water pump 12, and bears most of indoor sensible heat cooling load from the end of the demand response time period to the end of the occupation time period.
One specific application scenario of the present invention is described in detail below:
taking a certain office building as an example, the system matched with the building is the refrigerating system, the indoor heat exchange tail end of the temperature control subsystem is a radiation ceiling, the working day occupation time period is 8-00, the demand response time period is 13-00.
The method comprises the steps of firstly, collecting historical operation data of a temperature control subsystem, wherein the historical operation data comprises high-temperature water chilling unit operation data, second circulating water pump operation data, third circulating water pump operation data, indoor set temperature in an air conditioning period, indoor actual temperature in the air conditioning period and indoor heat exchange tail end water supply and return temperature, acquiring outdoor meteorological parameters including outdoor air dry bulb temperature, outdoor air relative humidity and solar radiation intensity in corresponding periods through relevant meteorological websites, acquiring parameters such as work and rest of indoor personnel and equipment through a fixed work and rest table of an office building, dividing the parameters into a model training set and a model verification set according to time periods, constructing a support vector regression load prediction model, and predicting the hourly cooling load born by the temperature control subsystem in the next day by using the load prediction model.
And step two, determining the theoretical cold accumulation amount of the cold accumulation water tank according to the predetermined demand response time interval and the predicted hourly cooling load born by the temperature control subsystem.
And thirdly, checking the theoretical cold storage amount and the actual maximum cold storage amount of the cold storage water tank and determining the optimal operation scheme of the demand response time period.
When the theoretical cold storage amount of the cold storage water tank is smaller than the actual maximum cold storage amount of the cold storage water tank, the scheme A is adopted in the operation scheme of the demand response time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller in the non-occupation time period, the stored cold amount is the theoretical cold storage amount of the cold storage water tank, and the stored cold amount is controlled to reach the theoretical cold storage amount of the cold storage water tank through the operation time of the high-temperature water chiller.
The specific operation of scheme a is as follows: considering that the radiation ceiling is easy to have a condensation phenomenon in the early stage of a refrigeration period, the working day occupies the previous hour of the period, namely 7, the water chilling unit, the first electromagnetic valve and the first circulating water pump receive a control signal from the controller to refrigerate and dehumidify fresh air, and the fresh air is sent to the indoor space by the power device to bear 7. The working day occupies the starting moment of the time period, namely 8 00, and the high-temperature water chilling unit, the second electromagnetic valve and the second circulating water pump receive a control signal from the controller, pump the high-temperature chilled water to the radiation ceiling through the second circulating water, and bear most of indoor sensible heat cold load from 8-00, namely occupy most indoor sensible heat cold load from the starting moment of the time to the starting moment of the demand response time period. At the beginning moment of the demand response period, namely 13, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are closed, the fourth electromagnetic valve and the third circulating water pump are opened, the cold accumulation water tank pumps the high-temperature chilled water to the radiation ceiling through the third circulating water, and most of sensible heat cold loads in the room of 13-00, namely most sensible heat cold loads in the room of the demand response period are born. At the end of the demand response time period, namely 15 00, the fourth electromagnetic valve and the third circulating water pump are closed, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are opened, and the high-temperature water chilling unit pumps high-temperature chilled water to the radiation ceiling through the second circulating water to bear most of sensible heat cooling load in the 15-00. And (4) closing all the coolers, the electromagnetic valves and the water pumps at the end moment of the occupation period, namely 18.
Influenced by outdoor meteorological parameters, when the actual maximum cold storage amount of the cold storage water tank is close to but can not meet the theoretical cold storage amount of the cold storage water tank, the scheme B is adopted in the operation scheme of the demand response time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller in the non-occupation time period, and the stored cold amount is the actual maximum cold storage amount of the cold storage water tank. And obtaining the cold release time length of the cold storage water tank through a cold release time length calculation formula, and determining the advanced starting time of the high-temperature water chilling unit, wherein the advanced starting time is 0.2 hour if the cold release time length is 1.8 hours.
The specific operation of scheme B is as follows: considering that the radiation ceiling is easy to have a condensation phenomenon in the early stage of a refrigeration period, the working day occupies the previous hour of the period, namely 7, the water chilling unit, the first electromagnetic valve and the first circulating water pump receive a control signal from the controller to refrigerate and dehumidify fresh air, and the fresh air is sent to the indoor space by the power device to bear 7. The working day occupies the initial time of the time period, namely 8 00, the high-temperature water chilling unit, the second electromagnetic valve and the second circulating water pump receive a control signal from the controller, pump the high-temperature chilled water to the radiation ceiling through the second circulating water, and bear most of indoor sensible heat cooling load from 8-00, namely occupy most of indoor sensible heat cooling load from the initial time of the time period to the initial time of the demand response time period. At the beginning of the demand response period, namely 13, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are closed, the fourth electromagnetic valve and the third circulating water pump are opened, and the cold accumulation water tank pumps high-temperature chilled water to the radiation ceiling through the third circulating water to bear most of sensible heat cold load in the room of 13-00. And 14, closing the fourth electromagnetic valve and the third circulating water pump, opening the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve, pumping high-temperature chilled water to the radiation ceiling through the second circulating water by the high-temperature water chilling unit, and bearing most of sensible heat cooling load in the room of 14-48. And (4) closing all the coolers, the electromagnetic valves and the water pumps at the end moment of the occupation period, namely 18.
Under the influence of outdoor meteorological parameters, when the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount of the cold storage water tank and the high-temperature water chilling unit is too long in starting time in advance, for example, the cold release time is 1 hour, the starting time in advance is 1 hour, the cold release time accounts for half of the demand response time period, the demand response potential of the system cannot be fully utilized, the demand response time period operation scheme adopts a scheme C, the cold storage water tank is subjected to cold storage through the high-temperature water chilling unit in the non-occupied time period, and the stored cold amount is the actual maximum cold storage amount of the cold storage water tank. Within the acceptable range of indoor thermal comfort, the indoor set temperature in the next day demand response period is increased to 27 ℃, and the cold release duration is recalculated to meet the requirement of the demand response period.
The specific operation of scheme C is as follows: considering that the radiation ceiling is easy to have a condensation phenomenon in the early stage of a refrigeration period, the working day occupies the previous hour of the period, namely 7, the water chilling unit, the first electromagnetic valve and the first circulating water pump receive a control signal from the controller to refrigerate and dehumidify fresh air, and the fresh air is sent to the indoor space by the power device to bear 7. The working day occupies the starting time of the time period, namely 8 00 ℃, the high-temperature water chilling unit, the second electromagnetic valve and the second circulating water pump receive a control signal from the controller, pump the high-temperature chilled water to the radiation ceiling through the second circulating water, bear most of sensible heat cooling load in 8-00. At the beginning of the demand response period, namely 13, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are closed, the fourth electromagnetic valve and the third circulating water pump are opened, the cold accumulation water tank pumps high-temperature chilled water to the radiation ceiling through the third circulating water, and the high-temperature chilled water pump bears most of sensible heat cold load in a 00-00 room and maintains the room temperature at about 27 ℃.15, the fourth electromagnetic valve and the third circulating water pump are closed, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are opened, the high-temperature water chilling unit pumps high-temperature chilled water to the radiation ceiling through second circulating water, most of sensible heat cooling load in a room of 15-00 ℃ is borne, and the room temperature is maintained at about 25 ℃. And (4) closing all the coolers, the electromagnetic valves and the water pumps at the end moment of the occupation period, namely 18.
Under the extremely severe weather condition, the requirement of the demand response time period can not be met after the scheme C is adopted, the scheme D is adopted in the demand response time period operation scheme, the cold storage water tank is subjected to cold storage through the high-temperature water chiller in the non-occupied time period, and the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank. And in the demand response period of the next day, the indoor set temperature is increased to the highest temperature within the acceptable range of thermal comfort, such as 29 ℃, the cold release time length of the cold storage water tank is obtained through a cold release time length calculation formula, and the advanced start-up time of the high-temperature water chilling unit is determined, such as the cold release time length is 1.5 hours, and the advanced start-up time is 0.5 hours.
The specific operation of scheme D is as follows: considering that the radiation ceiling is easy to have a condensation phenomenon in the early stage of a refrigeration period, the working day occupies the previous hour of the period, namely 7, the water chilling unit, the first electromagnetic valve and the first circulating water pump receive a control signal from the controller to refrigerate and dehumidify fresh air, and the fresh air is sent to the indoor space by the power device to bear 7. The working day occupies the starting moment of the time period, namely 8 00, the high-temperature water chilling unit, the second electromagnetic valve and the second circulating water pump receive a control signal from the controller, the high-temperature chilled water is pumped to the radiation ceiling through the second circulating water, most of sensible heat cold loads in the room of 8-00 are borne, namely most sensible heat cold loads in the room from the occupying time starting moment to the requiring response time period starting moment are occupied, and the room temperature is maintained at about 25 ℃. At the beginning of the demand response period, namely 13, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are closed, the fourth electromagnetic valve and the third circulating water pump are opened, the cold accumulation water tank pumps high-temperature chilled water to the radiation ceiling through the third circulating water, and the high-temperature chilled water tank bears most of sensible heat cold load in a 30-00 chamber and maintains the room temperature at about 29 ℃.14, the fourth electromagnetic valve and the third circulating water pump are closed, the high-temperature water chilling unit, the second circulating water pump and the second electromagnetic valve are opened, the high-temperature water chilling unit pumps high-temperature chilled water to the radiation ceiling through second circulating water, most of sensible heat cooling load in a room of 14-18 ℃ is borne, and the room temperature is maintained at about 25 ℃. And (4) closing all the coolers, the electromagnetic valves and the water pumps at the end moment of the occupation period, namely 18.
The above description is only an embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (9)
1. A demand response control method for an air conditioner capable of independently controlling temperature and humidity is characterized in that: the method comprises the following steps:
step one, forecasting hourly cooling load born by a temperature control subsystem on the next day by using a support vector regression model;
secondly, determining the theoretical cold accumulation amount of the cold accumulation water tank according to the predetermined demand response time period and the predicted hourly cold load borne by the temperature control subsystem;
checking the theoretical cold accumulation amount and the actual maximum cold accumulation amount of the cold accumulation water tank, evaluating the feasibility of various operation schemes, and further determining the optimal operation scheme in the demand response period; the steps for determining the optimal operation scheme in the demand response period are as follows:
if the actual maximum cold storage amount of the cold storage water tank can meet the theoretical cold storage amount, a scheme A is adopted for the operation strategy in the response time period; the scheme A specifically comprises the following steps: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the theoretical cold storage quantity of the cold storage water tank, and the cold quantity required by the temperature control subsystem is provided through the cold storage water tank in the response time period;
if the actual maximum cold storage amount of the cold storage water tank is close to but cannot meet the theoretical cold storage amount, calculating the cold release time of the cold storage water tank, determining the advanced starting time of the high-temperature water chilling unit, and adopting a scheme B in a demand response time interval operation strategy; the scheme B specifically comprises the following steps: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the difference value of the cold release time length, the demand response time period and the cold release time length is calculated, the advanced starting time of the high-temperature water chiller is determined, and the cold quantity required by the temperature control subsystem is provided by the cold storage water tank and the high-temperature water chiller in sequence in the demand response time period;
if the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount and the starting time of the high-temperature water chilling unit is too long in advance, a scheme C is adopted for the operation strategy in the demand response period; the scheme C specifically comprises the following steps: in the non-occupation time period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the indoor set temperature in the demand response time period is increased based on the acceptable range of indoor thermal comfort, the requirement of the demand response time period can be met until the cold release time of the cold storage water tank at the current indoor set temperature is long, and the cold quantity required by the temperature control subsystem is provided through the cold storage water tank in the demand response time period;
if the actual maximum cold storage amount of the cold storage water tank cannot meet the theoretical cold storage amount and the possibility that the requirement of the demand response time period cannot be met is still considered in the case of adopting the scheme C under the extremely severe weather condition, adopting a scheme D by the operation strategy of the demand response time period; the scheme D specifically comprises the following steps: and in the non-occupied period, the cold storage water tank is subjected to cold storage through the high-temperature water chiller, the stored cold quantity is the actual maximum cold storage quantity of the cold storage water tank, the highest temperature is taken as the indoor set temperature of the demand response period within the acceptable range of indoor thermal comfort, the difference value of the cold release time, the demand response period and the cold release time is calculated, the advanced startup time of the high-temperature water chiller is determined, and the cold quantity required by the temperature control subsystem is provided by the cold storage water tank and the high-temperature water chiller in sequence in the demand response period.
2. The demand response control method for the temperature and humidity independent control air conditioner according to claim 1, wherein the collection of relevant parameters in the first step includes historical time-by-time cooling load borne by the temperature control subsystem, outdoor meteorological parameters and indoor personnel equipment work and rest as input parameters, and the time-by-time cooling load borne by the temperature control subsystem on the next day is predicted through a support vector regression model.
3. The demand response control method for the temperature and humidity independent control air conditioner according to claim 1, wherein the theoretical cold storage amount of the cold storage water tank in the second step refers to a theoretically required cold storage amount of the temperature control subsystem in a demand response period, and a calculation formula is as follows:
wherein Q is i For theoretical cold storage capacity of cold storage water tank, Q CL (t) predicted time-by-time cooling load of the next day, t 1 For the start of the demand response period, t 2 The end time of the demand response period.
4. The demand response control method for the temperature and humidity independent control air conditioner as claimed in claim 1, wherein the actual maximum cool storage capacity of the cool storage water tank in the third step is limited by the effective volume of the cool storage water tank and the design condition of the temperature control subsystem, and the theoretical cool storage capacity and the actual maximum cool storage capacity of the cool storage water tank need to be checked when the theoretical cool storage capacity requirement cannot be met.
5. The demand response control method for the temperature and humidity independent control air conditioner as claimed in claim 1, wherein the actual maximum cool storage amount of the cool storage water tank in step three is calculated by the following formula:
Q a ＝C p ρVΔT a η 1
wherein Q is a Is the actual maximum cold storage amount of the cold storage water tank, C p Is the specific heat capacity of the cold storage liquid in the cold storage water tank, rho is the density of the liquid in the cold storage water tank, V is the effective volume of the cold storage water tank, and delta T a The temperature difference eta of the fluid at the inlet and the outlet of the cold accumulation water tank under the design working condition 1 The heat preservation efficiency of the cold accumulation water tank is improved.
6. The demand response control method of the temperature and humidity independent control air conditioner as claimed in claim 1, wherein in step three, the cold release time calculation formula of the cold storage water tank is as follows:
t d ＝(V/v)×(ΔT a /ΔT d )
wherein, t d The duration of cold release of the cold storage water tank, V is the effective volume of the cold storage water tank, V is the volume flow of the chilled water when the cold storage water tank releases cold in the demand response period, and delta T a For designing the temperature difference, delta T, of the fluid at the inlet and the outlet of the cold accumulation water tank under the working condition d The temperature difference of the water supply and the water return at the indoor heat exchange tail end of the temperature control subsystem.
7. The utility model provides a humiture independent control air conditioner refrigerating system which characterized in that: comprises a controller, a humidity control subsystem and a temperature control subsystem; the humidity control subsystem comprises a water chilling unit, a circulating water pump and a dehumidifying fresh air unit; the temperature control subsystem comprises a high-temperature water chilling unit, a circulating water pump, a cold accumulation water tank and an indoor heat exchange tail end; the high-temperature water chilling unit is respectively connected with the indoor heat exchange tail end and the cold accumulation water tank through the water supply branch pipe, the indoor heat exchange tail end and the cold accumulation water tank are respectively connected with the circulating water pump through the water return branch pipe, a water return supply passage is additionally arranged between the cold accumulation water tank and the indoor heat exchange tail end, electromagnetic valves are respectively arranged on the water return supply branch pipes, and the electromagnetic valves receive control signals from the controller and are used for controlling the on-off of the water path.
8. The air conditioning and refrigerating system with independent temperature and humidity control as claimed in claim 7, wherein the air conditioning and refrigerating system comprises: the indoor heat exchange tail end is a radiation ceiling or a dry type fan coil.
9. The air conditioning and refrigerating system with independent temperature and humidity control as claimed in claim 7, wherein the air conditioning and refrigerating system comprises: chilled water provided by a water chilling unit in the humidity control subsystem is sent to a dehumidifying fresh air unit by a circulating water pump, the dehumidifying fresh air unit refrigerates and dehumidifies fresh air, and the fresh air is sent to the indoor by a power device to bear all latent heat cold load and part sensible heat cold load; chilled water provided by a high-temperature water chilling unit in the temperature control subsystem is respectively sent to the indoor heat exchange tail end and the cold accumulation water tank by the circulating water pump based on control signals of the controller at different time intervals, and most of indoor sensible heat cold load is borne.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210795343.6A CN115143558B (en) | 2022-07-07 | 2022-07-07 | Air conditioner demand response control method and refrigeration system capable of independently controlling temperature and humidity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210795343.6A CN115143558B (en) | 2022-07-07 | 2022-07-07 | Air conditioner demand response control method and refrigeration system capable of independently controlling temperature and humidity |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115143558A true CN115143558A (en) | 2022-10-04 |
| CN115143558B CN115143558B (en) | 2024-03-05 |
Family
ID=83412015
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210795343.6A Active CN115143558B (en) | 2022-07-07 | 2022-07-07 | Air conditioner demand response control method and refrigeration system capable of independently controlling temperature and humidity |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115143558B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1924473A (en) * | 2006-09-22 | 2007-03-07 | 上海华电源牌环境工程有限公司 | Temperature and humidity individual control air conditioner system |
| CN103438545A (en) * | 2013-09-06 | 2013-12-11 | 肖剑仁 | Conventional composite cold and heat source coupled water-cold-storage air conditioning system based on independent temperature and humidity control and application method thereof |
| CN107014011A (en) * | 2017-03-23 | 2017-08-04 | 西安工程大学 | Evaporative Cooling Air-conditioning System based on temperature humidity independent control |
| CN107355926A (en) * | 2017-07-11 | 2017-11-17 | 福建省建筑设计研究院 | High-temperature refrigeration coupling accumulation of energy cold source air conditioning system and its control method based on independent temperature-humidity control |
| CN208296156U (en) * | 2018-02-12 | 2018-12-28 | 深圳市云科设计咨询服务有限公司 | With transpiration-cooled independent temperature-humidity control system |
| CN112815395A (en) * | 2021-01-20 | 2021-05-18 | 东南大学常州研究院 | Multi-connection radiation supply air conditioning system with temperature and humidity independently controlled |
-
2022
- 2022-07-07 CN CN202210795343.6A patent/CN115143558B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1924473A (en) * | 2006-09-22 | 2007-03-07 | 上海华电源牌环境工程有限公司 | Temperature and humidity individual control air conditioner system |
| CN103438545A (en) * | 2013-09-06 | 2013-12-11 | 肖剑仁 | Conventional composite cold and heat source coupled water-cold-storage air conditioning system based on independent temperature and humidity control and application method thereof |
| CN107014011A (en) * | 2017-03-23 | 2017-08-04 | 西安工程大学 | Evaporative Cooling Air-conditioning System based on temperature humidity independent control |
| CN107355926A (en) * | 2017-07-11 | 2017-11-17 | 福建省建筑设计研究院 | High-temperature refrigeration coupling accumulation of energy cold source air conditioning system and its control method based on independent temperature-humidity control |
| CN208296156U (en) * | 2018-02-12 | 2018-12-28 | 深圳市云科设计咨询服务有限公司 | With transpiration-cooled independent temperature-humidity control system |
| CN112815395A (en) * | 2021-01-20 | 2021-05-18 | 东南大学常州研究院 | Multi-connection radiation supply air conditioning system with temperature and humidity independently controlled |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115143558B (en) | 2024-03-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Ortiz et al. | Modeling of a solar-assisted HVAC system with thermal storage | |
| Marc et al. | Experimental investigation of a solar cooling absorption system operating without any backup system under tropical climate | |
| CA2445970C (en) | Air-conditioning system | |
| CN202613835U (en) | Simultaneous cold and heat supply energy-saving system | |
| Cole et al. | Use of model predictive control to enhance the flexibility of thermal energy storage cooling systems | |
| Barone et al. | WLHP systems in commercial buildings: A case study analysis based on a dynamic simulation approach | |
| CN104197446A (en) | Dynamic double-cold-source pre-cooling energy-saving air conditioning system | |
| US11680733B2 (en) | Storage source and cascade heat pump systems | |
| CN115143558B (en) | Air conditioner demand response control method and refrigeration system capable of independently controlling temperature and humidity | |
| CN214757525U (en) | Data center air conditioning system capable of utilizing natural cold source all year round | |
| CN111928428B (en) | Control method of air conditioning system considering demand response and refrigeration system | |
| CN104776636A (en) | Multi-unstable-cold-and-heat-source joint cooling and heating water mixing system and cooling and heating method thereof | |
| JP5062555B2 (en) | Energy saving air conditioning control system | |
| CN204555422U (en) | Many unstable Cooling and Heat Source air conditioning heat supply turbid water system | |
| CN114240470A (en) | Method for measuring and calculating marginal contribution degree of diversified market main body | |
| CN203163134U (en) | Energy-saving water-cooling heat-pump air-conditioning device | |
| CN201259287Y (en) | Cold storage air conditioner system for enhancing cold-storage density | |
| CN205448100U (en) | Cold -storage cooling device | |
| Suri et al. | Experimental investigation of chilled water storage technique for peak power shaving | |
| CN210050907U (en) | Energy-saving cooling system | |
| CN203657121U (en) | Temperature adjusting system | |
| CN219140959U (en) | High-efficient cold-storage air conditioning system | |
| CN219976602U (en) | Water-cooling multi-connected air conditioning system for subway station | |
| CN218627475U (en) | Industrial water chilling unit | |
| CN117366792B (en) | Operation control method and system of cold accumulation air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |