CN111895588A - Optimization control method for combined air treatment unit - Google Patents

Optimization control method for combined air treatment unit Download PDF

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Publication number
CN111895588A
CN111895588A CN202010896454.7A CN202010896454A CN111895588A CN 111895588 A CN111895588 A CN 111895588A CN 202010896454 A CN202010896454 A CN 202010896454A CN 111895588 A CN111895588 A CN 111895588A
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air
cold water
pipe unit
water valve
rho
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CN111895588B (en
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陈铁虎
冯兰
阳季春
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Zhongke Maijin Energy Saving Technology Zhejiang Co ltd
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Zhongke Maijin Energy Saving Technology Zhejiang Co ltd
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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
    • 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
    • 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
    • F24F11/62—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
    • F24F11/65—Electronic processing for selecting an operating mode
    • 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
    • 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
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • 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
    • F24F3/044—Systems in which all treatment is given in the central station, i.e. all-air systems
    • 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
    • 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
    • F24F3/16—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 purification, e.g. by filtering; by sterilisation; by ozonisation
    • 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
    • F24F5/001—Compression cycle type
    • 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
    • F24F2110/10—Temperature
    • 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

Abstract

The invention discloses an optimal control method for a combined air treatment unit, which comprises a centralized control module, the combined air treatment unit, a six-pipe unit and a sensor. The optimal control method for the combined air treatment unit is simple in steps and convenient to use, and realizes enthalpy and humidity optimal control of the combined air treatment unit by presetting parameters, controlling each component by means of the centralized control module, installing the temperature and humidity sensor and accurately calculating the air treatment process of the combined air treatment unit, so that the combined air treatment unit is in the most energy-saving operation mode; the work efficiency of the combined air treatment unit is improved, and the energy consumption is reduced.

Description

Optimization control method for combined air treatment unit
Technical Field
The invention relates to the field of combined air treatment units, in particular to an optimization control method for a combined air treatment unit.
Background
The combined air processor is a novel combined air conditioning unit, is manufactured by applying advanced CAD auxiliary design and production process, has the characteristics of compact structure, attractive appearance, convenient installation and maintenance, good rigidity of the whole machine, small air leakage quantity and the like, can be widely applied to industrial air conditioners of electronic instruments, precision machinery manufacturing, textile, chemical fiber, cigarettes, pharmacy, food, power stations, light chemical industry and the like, and is also suitable for comfortable air conditioners of commercial and civil large and medium-sized public buildings such as commercial buildings, restaurants, supermarkets, movie theaters, gymnasiums, markets, restaurants, hotels, office buildings and the like. The control of the existing combined air treatment unit is heat-humidity coupling control: the conventional constant temperature and humidity air conditioning system generally adopts a heat and humidity coupling control method to cool and dehumidify air, the humidity (moisture content) of the processed air meets the requirement, but the temperature is too low, and the requirement of air supply temperature and humidity can be met only by reheating, the control method causes waste and loss of energy,
in the combined air treatment unit, still there are the problems: the currently adopted heat-moisture coupling control needs to be reheated after air is cooled and dehumidified, so that energy waste and loss are caused to a certain extent.
Based on the above situation, the invention provides an optimal control method for a combined air treatment unit, which can effectively solve the above problems.
Disclosure of Invention
The invention aims to provide an optimal control method for a combined air treatment unit. The optimal control method for the combined air treatment unit is simple in steps and convenient to use, and realizes enthalpy and humidity optimal control of the combined air treatment unit by presetting parameters, controlling each component by means of the centralized control module, installing the temperature and humidity sensor and accurately calculating the air treatment process of the combined air treatment unit, so that the combined air treatment unit is in the most energy-saving operation mode; the work efficiency of the combined air treatment unit is improved, and the energy consumption is reduced.
The invention is realized by the following technical scheme:
an optimal control method for a combined air handling unit, comprising: the method comprises the following steps:
step S1: setting calculation parameters and a method in a centralized control module in advance;
step S2: calculating a fresh air moisture content dx and a fresh air enthalpy value hx according to a fresh air temperature Tx and a fresh air relative humidity Rhx acquired by a fresh air temperature and humidity sensor;
step S3: calculating the moisture content dh and enthalpy hh of the return air through the return air temperature Th and the return air relative humidity RHh acquired by the return air temperature and humidity sensor;
step S4: calculating the moisture content dm and the enthalpy value hm of the mixed wind according to the temperature Tm and the relative humidity Rhm of the mixed wind acquired by the temperature and humidity sensor of the mixed wind;
step S5: calculating the inlet air moisture content dj and the inlet air enthalpy hj of the six-pipe unit through the inlet air temperature Tj of the six-pipe unit and the inlet air relative humidity RHj of the six-pipe unit, which are acquired by the inlet air temperature and humidity sensor of the six-pipe unit;
step S6: calculating the outlet air moisture content dc of the six-pipe unit and the outlet air enthalpy value hc of the six-pipe unit through the outlet air temperature Tc of the six-pipe unit and the outlet air relative humidity RHc of the six-pipe unit, which are acquired by the outlet air temperature and humidity sensor of the six-pipe unit;
step S7: calculating the air supply moisture content ds and the air supply enthalpy hs through the air supply temperature Ts and the air supply relative humidity Rhs acquired by the air supply temperature and humidity sensor;
step S8: the indoor temperature Tn and the indoor relative humidity RHn are acquired by an indoor temperature and humidity sensor;
step S9: presetting an indoor target temperature Ta and an indoor target relative humidity RHA, and calculating an indoor target moisture content da;
step S10: presetting air supply quantity F and air density rho;
step S11: presetting an indoor differential pressure value delta P, and calculating a fresh air volume Fx;
step S12: after the cold or heat load Q and the humidity load W of the air conditioning area are calculated through the following formulas, the processing mode of the combined air processing unit is judged and selected:
q1+ Q2, Q1 is the cold or heat load of the air-conditioning area in the detection period t, Q1 is ρ (F-Fx) hh-hs) t, Q2 is the new air-cooling or heat load in the detection period t, Q2 is ρ Fx (hx-hs) t;
w1+ W2, W1 is the humidity load of the air conditioning region in the detection period t, W1 is ρ (F-Fx) × (dh-ds) × t, W2 is the fresh air humidity load in the detection period t, and W2 is ρ × Fx (dx-ds) × t;
step S121: if Q is less than 0 and W is less than 0, the combined air processing unit selects a heating and humidifying mode;
step S122: if Q is less than 0 and W is more than 0, the combined air handling unit selects a heating and dehumidifying mode;
step S123: if Q is less than 0, W is 0, the combined air processing unit selects a heating mode;
step S124: if Q is more than 0 and W is less than 0, the combined air handling unit selects a cooling and humidifying mode;
step S125: if Q is more than 0 and W is more than 0, the combined air handling unit selects a cooling and dehumidifying mode;
step S126: if Q is larger than 0, W is 0, the combined air handling unit selects a cooling mode;
step S127: if Q is 0 and W is less than 0, the combined air handling unit selects a humidifying mode;
step S128: if Q is 0 and W is more than 0, the combined air handling unit selects a dehumidification mode;
step S129: if Q is 0 and W is 0, the combined air handling unit selects a balance mode;
step 13: the centralized control center compares the actually measured indoor temperature Tn and indoor relative humidity RHn with the indoor target temperature Ta and the indoor target relative humidity RHA;
step 14: and carrying out fine adjustment on the fresh air cold water valve, the mixed cold water valve, the six-pipe unit compressor, the six-pipe unit balance pump, the heating steam valve and the humidifying steam valve according to the compared actual conditions.
The invention aims to provide an optimal control method for a combined air treatment unit. The optimal control method for the combined air treatment unit is simple in steps and convenient to use, and realizes enthalpy and humidity optimal control of the combined air treatment unit by presetting parameters, controlling each component by means of the centralized control module, installing the temperature and humidity sensor and accurately calculating the air treatment process of the combined air treatment unit, so that the combined air treatment unit is in the most energy-saving operation mode; the work efficiency of the combined air treatment unit is improved, and the energy consumption is reduced.
Preferably, step S121 is specifically as follows:
step S1211: closing the fresh air cold water valve, the mixed cold water valve and the six-pipe unit, and opening the heating steam valve and the humidifying steam valve;
step S1212: the opening degree of the heating steam valve is correspondingly adjusted according to the value of the heat load Q, and the opening degree of the humidifying steam valve is correspondingly adjusted according to the value of the humidity load W.
Preferably, step S122 is specifically as follows:
step S1221: closing the fresh air cold water valve, closing the mixed cold water valve, closing the heating steam valve, closing the humidifying steam valve, and opening the six-pipe unit;
step S12211: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12212: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12213: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1222: if Tn is larger than or equal to Ta, starting a balance pump of the six-pipe unit, and adjusting the frequency of the balance pump of the six-pipe unit;
step S1223: if Tn is less than Ta, the balance pump of the six-pipe unit is closed, and the opening of the heating steam valve is adjusted.
Preferably, step S123 specifically includes the following steps:
step S1231: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the humidifying steam valve, and opening the heating steam valve;
step S1232: and correspondingly adjusting the opening degree of the heating steam valve according to the numerical value of the heat load Q.
Preferably, step S124 specifically includes the following steps:
step S1241: closing the fresh air cold water valve, the six-pipe unit and the heating steam valve, and opening the mixed cold water valve and the humidifying steam valve;
step S1242: and adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q, and adjusting the opening of the humidifying steam valve according to the numerical value of the wet load W.
Preferably, step S125 is specifically as follows:
step S1251: closing the fresh air cold water valve, the mixed cold water valve, the heating steam valve and the humidifying steam valve, and opening the six-pipe unit;
step S12511: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12512: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12513: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1252: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
Preferably, step S126 specifically includes the following steps:
step S1261: closing the fresh air cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve, and opening the mixing cold water valve;
step S1262: and correspondingly adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q.
Preferably, step S127 is specifically as follows:
step S1271: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the heating steam valve, and opening the humidifying steam valve;
step S1272: and correspondingly adjusting the humidifying steam valve according to the value of the wet load W.
Preferably, step S128 is specifically as follows:
step S1281: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S1282: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S1283: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1284: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
Preferably, step S129 specifically includes the following steps:
step S1291: and closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve.
Preferably, the control method is applied to an optimized control system for a combined air treatment unit, and comprises the following steps:
the combined air handling unit comprises a fresh air section, a fresh air meter cooling section, an air return section, a mixing section, a primary effect filtering section, a mixing meter cooling section, an overhauling section, a steam heating section, a steam humidifying section, an air feeder section, a flow equalizing section, a middle effect filtering section, an air feeding section and an indoor temperature and humidity sensor;
the fresh air section is provided with a fresh air inlet pipe and a fresh air outlet pipe, and a fresh air temperature and humidity sensor is arranged on the fresh air inlet pipe; the air return section is provided with an air return inlet pipe and an air return outlet pipe, and the air return inlet pipe is provided with an air return temperature and humidity sensor; the mixing section is provided with a fresh air inlet, a return air inlet and an air outlet, and a mixed air temperature and humidity sensor is arranged in the mixing section; the air supply section is provided with an air supply pipe, and an air supply temperature and humidity sensor is arranged on the air supply pipe;
the condensation heat recovery device comprises an air inlet pipe and an air outlet pipe, wherein the air inlet pipe is communicated with the maintenance section, an air inlet temperature and humidity sensor is arranged on the air inlet pipe, the air outlet pipe is communicated with the air feeder section, and an air outlet temperature and humidity sensor is arranged on the air outlet pipe;
the centralized control module is used for controlling the components of the whole system, and is respectively and electrically connected with the condensation heat recovery device, the fresh air temperature and humidity sensor, the return air temperature and humidity sensor, the mixed air temperature and humidity sensor, the air supply temperature and humidity sensor, the air inlet temperature and humidity sensor, the air outlet temperature and humidity sensor and the indoor temperature and humidity sensor;
the fresh air outlet pipe of the fresh air section is communicated with one side of the cold section of the fresh air meter, the other side of the cold section of the fresh air meter is communicated with the fresh air inlet of the mixing section, the return air outlet pipe of the return air section is communicated with the return air inlet of the mixing section, and the air outlet of the mixing section is communicated with the primary effect filtering section;
the mixing section, the primary effect filtering section, the mixing surface cooling section, the maintenance section, the steam heating section, the steam humidifying section, the air feeder section, the flow equalizing section, the intermediate effect filtering section and the air feeding section are communicated in sequence.
It is also an object of the present invention to provide an optimized control system for a modular air handling unit. The optimization control system for the combined air treatment unit is simple in structure and convenient to use, and by presetting parameters, controlling each part by means of the centralized control module, installing the temperature and humidity sensors and accurately calculating the air treatment process of the combined air treatment unit, the enthalpy and humidity optimization control of the combined air treatment unit is realized, and the combined air treatment unit is in the most energy-saving operation mode; the work efficiency of the combined air treatment unit is improved, and the energy consumption is reduced.
Preferably, the cold section of the fresh air meter is provided with a first water return pipe, the first water return pipe is provided with a fresh air cold water valve, and the fresh air cold water valve is electrically connected with the centralized control module.
Preferably, the mixed surface cooling section is provided with a second water return pipe, the second water return pipe is provided with a mixed cold water valve, and the mixed cold water valve is electrically connected with the centralized control module.
Preferably, the steam heating section is provided with a first steam supply pipe, the first steam supply pipe is provided with a heating steam valve, and the heating steam valve is electrically connected with the centralized control module.
Preferably, the steam humidifying section is provided with a second steam supply pipe, the second steam supply pipe is provided with a humidifying steam valve, and the humidifying steam valve is electrically connected with the centralized control module.
Preferably, the condensation heat recovery device is a six-pipe unit and comprises an evaporation section, a compressor, a condensation section, an expansion valve, a balance water pump and a fan.
Preferably, the centralized control module is electrically connected with the compressor, the balance water pump and the fan respectively.
Compared with the prior art, the invention has the following advantages and beneficial effects:
the optimal control method for the combined air treatment unit is simple in steps and convenient to use, and realizes enthalpy and humidity optimal control of the combined air treatment unit by presetting parameters, controlling each component by means of the centralized control module, installing the temperature and humidity sensor and accurately calculating the air treatment process of the combined air treatment unit, so that the combined air treatment unit is in the most energy-saving operation mode; the work efficiency of the combined air treatment unit is improved, and the energy consumption is reduced.
1. The newly-added six-pipe unit mainly bears the humidity load of an air conditioning area, the six-pipe unit is used for dehumidification, the dehumidification effect is more obvious due to the lower evaporation temperature, and meanwhile, the condensation heat recovery of the six-pipe unit replaces the steam reheating of a conventional constant-temperature constant-humidity unit, so that the use amount of steam is reduced, and the energy consumption can be reduced by about 20%;
2. the mixed surface cooling section mainly bears sensible heat of an air conditioning area, so that the mixed surface cooling section can adopt a high-temperature cold source to exhaust indoor heat, the high-temperature cold source adopts a water supply temperature of 11 ℃ and a water return temperature of 16 ℃, the water outlet temperature is increased, and the efficiency of a refrigeration host machine is improved by about 18%.
Drawings
FIG. 1 is a schematic flow diagram of the present invention;
FIG. 2 is a schematic diagram of an optimized control system for a modular air handling unit according to the present invention;
fig. 3 is a schematic structural diagram of a six-pipe unit according to the present invention.
Detailed Description
In order that those skilled in the art will better understand the technical solutions of the present invention, the following description of the preferred embodiments of the present invention is provided in conjunction with specific examples, but it should be understood that the drawings are for illustrative purposes only and should not be construed as limiting the patent; for the purpose of better illustrating the embodiments, certain features of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted. The positional relationships depicted in the drawings are for illustrative purposes only and are not to be construed as limiting the present patent.
Example 1:
as shown in fig. 1 to 3, the present invention provides an optimal control method for a combined air handling unit, including: the method comprises the following steps:
step S1: setting calculation parameters and a method in a centralized control module in advance;
step S2: the fresh air moisture content dx and the fresh air enthalpy value hx are calculated according to the fresh air temperature Tx and the fresh air relative humidity Rhx acquired by the fresh air temperature and humidity sensor, and the calculation formula is as follows (the following calculation formula of the moisture content and enthalpy value is not listed again):
Figure BDA0002658552490000081
(P represents air pressure (Pa) and Ps represents partial water vapor pressure (Pa));
hx is 1.01Tx + (2500+1.84Tx) dx, (1.01 represents the average specific heat at constant pressure of dry air (kj/(kg.k)), 1.84 represents the average specific heat at constant pressure of water vapor (kj/(kg.k)), and 2500 represents the latent heat of vaporization of water at 0 ℃ (kj/kg)).
Step S3: calculating the moisture content dh and enthalpy hh of the return air through the return air temperature Th and the return air relative humidity RHh acquired by the return air temperature and humidity sensor;
step S4: calculating the moisture content dm and the enthalpy value hm of the mixed wind according to the temperature Tm and the relative humidity Rhm of the mixed wind acquired by the temperature and humidity sensor of the mixed wind;
step S5: calculating the inlet air moisture content dj and the inlet air enthalpy hj of the six-pipe unit through the inlet air temperature Tj of the six-pipe unit and the inlet air relative humidity RHj of the six-pipe unit, which are acquired by the inlet air temperature and humidity sensor of the six-pipe unit;
step S6: calculating the outlet air moisture content dc of the six-pipe unit and the outlet air enthalpy value hc of the six-pipe unit through the outlet air temperature Tc of the six-pipe unit and the outlet air relative humidity RHc of the six-pipe unit, which are acquired by the outlet air temperature and humidity sensor of the six-pipe unit;
step S7: calculating the air supply moisture content ds and the air supply enthalpy hs through the air supply temperature Ts and the air supply relative humidity Rhs acquired by the air supply temperature and humidity sensor;
step S8: the indoor temperature Tn and the indoor relative humidity RHn are acquired by an indoor temperature and humidity sensor;
step S9: presetting an indoor target temperature Ta and an indoor target relative humidity RHA, and calculating an indoor target moisture content da;
step S10: presetting air supply quantity F and air density rho;
step S11: presetting an indoor differential pressure value delta P, and calculating a fresh air volume Fx;
step S12: after the cold or heat load Q and the humidity load W of the air conditioning area are calculated through the following formulas, the processing mode of the combined air processing unit is judged and selected:
q1+ Q2, Q1 is the cold or heat load of the air-conditioning area in the detection period t, Q1 is ρ (F-Fx) hh-hs) t, Q2 is the new air-cooling or heat load in the detection period t, Q2 is ρ Fx (hx-hs) t;
w1+ W2, W1 is the humidity load of the air conditioning region in the detection period t, W1 is ρ (F-Fx) × (dh-ds) × t, W2 is the fresh air humidity load in the detection period t, and W2 is ρ × Fx (dx-ds) × t;
step S121: if Q is less than 0 and W is less than 0, the combined air processing unit selects a heating and humidifying mode;
step S122: if Q is less than 0 and W is more than 0, the combined air handling unit selects a heating and dehumidifying mode;
step S123: if Q is less than 0, W is 0, the combined air processing unit selects a heating mode;
step S124: if Q is more than 0 and W is less than 0, the combined air handling unit selects a cooling and humidifying mode;
step S125: if Q is more than 0 and W is more than 0, the combined air handling unit selects a cooling and dehumidifying mode;
step S126: if Q is larger than 0, W is 0, the combined air handling unit selects a cooling mode;
step S127: if Q is 0 and W is less than 0, the combined air handling unit selects a humidifying mode;
step S128: if Q is 0 and W is more than 0, the combined air handling unit selects a dehumidification mode;
step S129: if Q is 0 and W is 0, the combined air handling unit selects a balance mode;
step 13: the centralized control center compares the actually measured indoor temperature Tn and indoor relative humidity RHn with the indoor target temperature Ta and the indoor target relative humidity RHA;
step 14: and carrying out fine adjustment on the fresh air cold water valve, the mixed cold water valve, the six-pipe unit compressor, the six-pipe unit balance pump, the heating steam valve and the humidifying steam valve according to the compared actual conditions.
Example 2:
as shown in fig. 1 to 3, the present invention provides an optimal control method for a combined air handling unit, including: the method comprises the following steps:
step S1: setting calculation parameters and a method in a centralized control module in advance;
step S2: the fresh air moisture content dx and the fresh air enthalpy value hx are calculated according to the fresh air temperature Tx and the fresh air relative humidity Rhx acquired by the fresh air temperature and humidity sensor, and the calculation formula is as follows (the following calculation formula of the moisture content and enthalpy value is not listed again):
Figure BDA0002658552490000101
(P represents air pressure (Pa) and Ps represents partial water vapor pressure (Pa));
hx is 1.01Tx + (2500+1.84Tx) dx, (1.01 represents the average specific heat at constant pressure of dry air (kj/(kg.k)), 1.84 represents the average specific heat at constant pressure of water vapor (kj/(kg.k)), and 2500 represents the latent heat of vaporization of water at 0 ℃ (kj/kg)).
Step S3: calculating the moisture content dh and enthalpy hh of the return air through the return air temperature Th and the return air relative humidity RHh acquired by the return air temperature and humidity sensor;
step S4: calculating the moisture content dm and the enthalpy value hm of the mixed wind according to the temperature Tm and the relative humidity Rhm of the mixed wind acquired by the temperature and humidity sensor of the mixed wind;
step S5: calculating the inlet air moisture content dj and the inlet air enthalpy hj of the six-pipe unit through the inlet air temperature Tj of the six-pipe unit and the inlet air relative humidity RHj of the six-pipe unit, which are acquired by the inlet air temperature and humidity sensor of the six-pipe unit;
step S6: calculating the outlet air moisture content dc of the six-pipe unit and the outlet air enthalpy value hc of the six-pipe unit through the outlet air temperature Tc of the six-pipe unit and the outlet air relative humidity RHc of the six-pipe unit, which are acquired by the outlet air temperature and humidity sensor of the six-pipe unit;
step S7: calculating the air supply moisture content ds and the air supply enthalpy hs through the air supply temperature Ts and the air supply relative humidity Rhs acquired by the air supply temperature and humidity sensor;
step S8: the indoor temperature Tn and the indoor relative humidity RHn are acquired by an indoor temperature and humidity sensor;
step S9: presetting an indoor target temperature Ta and an indoor target relative humidity RHA, and calculating an indoor target moisture content da;
step S10: presetting air supply quantity F and air density rho;
step S11: presetting an indoor differential pressure value delta P, and calculating a fresh air volume Fx;
step S12: after the cold or heat load Q and the humidity load W of the air conditioning area are calculated through the following formulas, the processing mode of the combined air processing unit is judged and selected:
q1+ Q2, Q1 is the cold or heat load of the air-conditioning area in the detection period t, Q1 is ρ (F-Fx) hh-hs) t, Q2 is the new air-cooling or heat load in the detection period t, Q2 is ρ Fx (hx-hs) t;
w1+ W2, W1 is the humidity load of the air conditioning region in the detection period t, W1 is ρ (F-Fx) × (dh-ds) × t, W2 is the fresh air humidity load in the detection period t, and W2 is ρ × Fx (dx-ds) × t;
step S121: if Q is less than 0 and W is less than 0, the combined air processing unit selects a heating and humidifying mode;
step S122: if Q is less than 0 and W is more than 0, the combined air handling unit selects a heating and dehumidifying mode;
step S123: if Q is less than 0, W is 0, the combined air processing unit selects a heating mode;
step S124: if Q is more than 0 and W is less than 0, the combined air handling unit selects a cooling and humidifying mode;
step S125: if Q is more than 0 and W is more than 0, the combined air handling unit selects a cooling and dehumidifying mode;
step S126: if Q is larger than 0, W is 0, the combined air handling unit selects a cooling mode;
step S127: if Q is 0 and W is less than 0, the combined air handling unit selects a humidifying mode;
step S128: if Q is 0 and W is more than 0, the combined air handling unit selects a dehumidification mode;
step S129: if Q is 0 and W is 0, the combined air handling unit selects a balance mode;
step 13: the centralized control center compares the actually measured indoor temperature Tn and indoor relative humidity RHn with the indoor target temperature Ta and the indoor target relative humidity RHA;
step 14: and carrying out fine adjustment on the fresh air cold water valve, the mixed cold water valve, the six-pipe unit compressor, the six-pipe unit balance pump, the heating steam valve and the humidifying steam valve according to the compared actual conditions.
Further, in another embodiment, step S121 is specifically as follows:
step S1211: closing the fresh air cold water valve, the mixed cold water valve and the six-pipe unit, and opening the heating steam valve and the humidifying steam valve;
step S1212: the opening degree of the heating steam valve is correspondingly adjusted according to the value of the heat load Q, and the opening degree of the humidifying steam valve is correspondingly adjusted according to the value of the humidity load W.
Preferably, step S122 is specifically as follows:
step S1221: closing the fresh air cold water valve, closing the mixed cold water valve, closing the heating steam valve, closing the humidifying steam valve, and opening the six-pipe unit;
step S12211: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12212: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12213: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1222: if Tn is larger than or equal to Ta, starting a balance pump of the six-pipe unit, and adjusting the frequency of the balance pump of the six-pipe unit;
step S1223: if Tn is less than Ta, the balance pump of the six-pipe unit is closed, and the opening of the heating steam valve is adjusted.
Further, in another embodiment, step S123 specifically includes the following steps:
step S1231: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the humidifying steam valve, and opening the heating steam valve;
step S1232: and correspondingly adjusting the opening degree of the heating steam valve according to the numerical value of the heat load Q.
Further, in another embodiment, step S124 specifically includes the following steps:
step S1241: closing the fresh air cold water valve, the six-pipe unit and the heating steam valve, and opening the mixed cold water valve and the humidifying steam valve;
step S1242: and adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q, and adjusting the opening of the humidifying steam valve according to the numerical value of the wet load W.
Further, in another embodiment, step S125 is specifically as follows:
step S1251: closing the fresh air cold water valve, the mixed cold water valve, the heating steam valve and the humidifying steam valve, and opening the six-pipe unit;
step S12511: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12512: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12513: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1252: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
Further, in another embodiment, step S126 is specifically as follows:
step S1261: closing the fresh air cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve, and opening the mixing cold water valve;
step S1262: and correspondingly adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q.
Further, in another embodiment, step S127 is specifically as follows:
step S1271: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the heating steam valve, and opening the humidifying steam valve;
step S1272: and correspondingly adjusting the humidifying steam valve according to the value of the wet load W.
Further, in another embodiment, step S128 is specifically as follows:
step S1281: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S1282: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S1283: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1284: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
Further, in another embodiment, step S129 is specifically as follows:
step S1291: and closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve.
Further, in another embodiment, the present control method is adapted for use in an optimized control system for a modular air handling unit, comprising:
combined air handling unit 100, including new trend section 101, new trend table cold section 102, return air section 103, mixing section 104, first effect filter segment 105, mixing table cold section 106, overhaul section 107, steam heating section 108, steam humidification section 109, air feeder section 110, the section 111 that flow equalizes, well effect filter segment 112, air supply section 113 and indoor temperature and humidity sensor 114, the position of indoor temperature and humidity sensor 114 installation again be convenient for, the debugging, maintenance work, and keep away from the blast pipe, the return air inlet tube, gate and wall body.
The fresh air section 101 is provided with a fresh air inlet pipe and a fresh air outlet pipe, and a fresh air temperature and humidity sensor 1011 is arranged on the fresh air inlet pipe; the return air section 103 is provided with a return air inlet pipe and a return air outlet pipe, and the return air inlet pipe is provided with a return air temperature and humidity sensor 1031; a fresh air inlet, a return air inlet and an air outlet are formed in the mixing section 104, and a mixed air temperature and humidity sensor 1041 is arranged in the mixing section 104; the air supply section 113 is provided with an air supply pipe, and an air supply temperature and humidity sensor 1131 is arranged on the air supply pipe;
the condensation heat recovery device 200 comprises an air inlet pipe and an air outlet pipe, wherein the air inlet pipe is communicated with the overhaul section 107, an air inlet temperature and humidity sensor 201 is arranged on the air inlet pipe, the air outlet pipe is communicated with the air feeder section 110, and an air outlet temperature and humidity sensor 202 is arranged on the air outlet pipe;
the centralized control module 300 is used for controlling components of the whole system, and can be a common technical means such as a PLC controller or a single chip microcomputer, and the centralized control module 300 is electrically connected with the condensation heat recovery device 200, the fresh air temperature and humidity sensor 1011, the return air temperature and humidity sensor 1031, the mixed air temperature and humidity sensor 1041, the supply air temperature and humidity sensor 1131, the supply air temperature and humidity sensor 201, the supply air temperature and humidity sensor 202 and the indoor temperature and humidity sensor 114 respectively;
the fresh air outlet pipe of the fresh air section 101 is communicated with one side of the fresh air meter cooling section 102, the other side of the fresh air meter cooling section 102 is communicated with the fresh air inlet of the mixing section 104, the return air outlet pipe of the return air section 103 is communicated with the return air inlet of the mixing section 104, and the air outlet of the mixing section 104 is communicated with the primary effect filtering section 105;
the mixing section 104, the primary effect filtering section 105, the mixing surface cooling section 106, the overhauling section 107, the steam heating section 108, the steam humidifying section 109, the air blower section 110, the flow equalizing section 111, the intermediate effect filtering section 112 and the air blowing section 113 are communicated in sequence.
Further, in another embodiment, the fresh air meter cooling section 102 is provided with a first water return pipe, the first water return pipe is provided with a fresh air cold water valve 1021, and the fresh air cold water valve 1021 is electrically connected with the centralized control module 300.
Further, in another embodiment, the hybrid surface cooling section 106 is provided with a second water return pipe, a hybrid cold water valve 1061 is provided on the second water return pipe, and the hybrid cold water valve 1061 is electrically connected with the centralized control module 300.
Further, in another embodiment, the steam heating section 108 is provided with a first steam supply pipe, the first steam supply pipe is provided with a heating steam valve 1081, and the heating steam valve 1081 is electrically connected with the centralized control module 300.
Further, in another embodiment, the steam humidification stage 109 is provided with a second steam supply pipe, the second steam supply pipe is provided with a humidification steam valve 1091, and the humidification steam valve 1091 is electrically connected to the centralized control module 300.
Due to the above structure, the centralized control module 300 can respectively control the opening degrees of the fresh air cold water valve 1021, the mixed cold water valve 1061, the heating steam valve 1081 and the humidifying steam valve 1091, so as to control the temperature and humidity of the air output from the air supply outlet, and achieve the preset target temperature and humidity.
Further, in another embodiment, the condensation heat recovery device 200 is a six-pipe unit, and includes an evaporation section 203, a compressor 204, a condensation section 205, an expansion valve 206, a balance water pump 207, and a fan 208.
The refrigerant in the evaporation section 203 evaporates and absorbs heat from the air, thereby lowering the air temperature, while the refrigerant in the condensation section 205 condenses and releases heat to heat the air, and the excess heat is carried away by the balance pump 207.
Further, in another embodiment, the centralized control module 300 is electrically connected to the compressor 204, the balance water pump 207, and the fan 208, respectively.
Due to the structure, the centralized control module 300 can respectively control the compressor 204, the balance water pump 207 and the fan 208, so as to control the working condition of the six-pipe unit.
The working principle of the optimal control system for the combined air treatment unit is as follows:
an optimized control system for a modular air handling unit:
indoor return air and outdoor fresh air respectively enter the mixing section 104 through the return air section 103 and the fresh air section 101;
after mixing, the mixture is sent to a primary filtering section 105 for primary filtering and purification;
after purification, part of the air enters the six-pipe unit 200, and the other part of the air enters the steam heating section 108, the steam humidifying section 109 and the air blower section 110 in sequence, and the two sections regulate the temperature and the humidity of the air according to different control modes;
after mixing, the mixture enters a flow equalizing section 111 to enable the passing wind to be uniformly distributed and flow;
then enters the middle-effect filtering section 112 for middle-level filtering and purification;
finally, the air is blown out through the air blowing section 113.
Unless otherwise specified, in the present invention, if there is an orientation or positional relationship indicated by terms of "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., based on the orientation or positional relationship shown in the drawings, it is only for convenience of describing the present invention and simplifying the description, rather than to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore, the terms describing orientation or positional relationship in the present invention are for illustrative purposes only, and should not be construed as limiting the present patent, specific meanings of the above terms can be understood by those of ordinary skill in the art in light of the specific circumstances in conjunction with the accompanying drawings.
Unless expressly stated or limited otherwise, the terms "disposed," "connected," and "connected" are used broadly and encompass, for example, being fixedly connected, detachably connected, or integrally connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications and equivalent variations of the above embodiments according to the technical spirit of the present invention are included in the scope of the present invention.

Claims (10)

1. An optimal control method for a combined air handling unit, comprising: the method comprises the following steps:
step S1: setting calculation parameters and a method in a centralized control module in advance;
step S2: calculating a fresh air moisture content dx and a fresh air enthalpy value hx according to a fresh air temperature Tx and a fresh air relative humidity Rhx acquired by a fresh air temperature and humidity sensor;
step S3: calculating the moisture content dh and enthalpy hh of the return air through the return air temperature Th and the return air relative humidity RHh acquired by the return air temperature and humidity sensor;
step S4: calculating the moisture content dm and the enthalpy value hm of the mixed wind according to the temperature Tm and the relative humidity Rhm of the mixed wind acquired by the temperature and humidity sensor of the mixed wind;
step S5: calculating the inlet air moisture content dj and the inlet air enthalpy hj of the six-pipe unit through the inlet air temperature Tj of the six-pipe unit and the inlet air relative humidity RHj of the six-pipe unit, which are acquired by the inlet air temperature and humidity sensor of the six-pipe unit;
step S6: calculating the outlet air moisture content dc of the six-pipe unit and the outlet air enthalpy value hc of the six-pipe unit through the outlet air temperature Tc of the six-pipe unit and the outlet air relative humidity RHc of the six-pipe unit, which are acquired by the outlet air temperature and humidity sensor of the six-pipe unit;
step S7: calculating the air supply moisture content ds and the air supply enthalpy hs through the air supply temperature Ts and the air supply relative humidity Rhs acquired by the air supply temperature and humidity sensor;
step S8: the indoor temperature Tn and the indoor relative humidity RHn are acquired by an indoor temperature and humidity sensor;
step S9: presetting an indoor target temperature Ta and an indoor target relative humidity RHA, and calculating an indoor target moisture content da;
step S10: presetting air supply quantity F and air density rho;
step S11: presetting an indoor differential pressure value delta P, and calculating a fresh air volume Fx;
step S12: after the cold or heat load Q and the humidity load W of the air conditioning area are calculated through the following formulas, the processing mode of the combined air processing unit is judged and selected:
q1+ Q2, Q1 is the cold or heat load of the air-conditioning area in the detection period t, Q1 is ρ (F-Fx) hh-hs) t, Q2 is the new air-cooling or heat load in the detection period t, Q2 is ρ Fx (hx-hs) t;
w1+ W2, W1 is the humidity load of the air conditioning region in the detection period t, W1 is ρ (F-Fx) × (dh-ds) × t, W2 is the fresh air humidity load in the detection period t, and W2 is ρ × Fx (dx-ds) × t;
step S121: if Q is less than 0 and W is less than 0, the combined air processing unit selects a heating and humidifying mode;
step S122: if Q is less than 0 and W is more than 0, the combined air handling unit selects a heating and dehumidifying mode;
step S123: if Q is less than 0, W is 0, the combined air processing unit selects a heating mode;
step S124: if Q is more than 0 and W is less than 0, the combined air handling unit selects a cooling and humidifying mode;
step S125: if Q is more than 0 and W is more than 0, the combined air handling unit selects a cooling and dehumidifying mode;
step S126: if Q is larger than 0, W is 0, the combined air handling unit selects a cooling mode;
step S127: if Q is 0 and W is less than 0, the combined air handling unit selects a humidifying mode;
step S128: if Q is 0 and W is more than 0, the combined air handling unit selects a dehumidification mode;
step S129: if Q is 0 and W is 0, the combined air handling unit selects a balance mode;
step 13: the centralized control center compares the actually measured indoor temperature Tn and indoor relative humidity RHn with the indoor target temperature Ta and the indoor target relative humidity RHA;
step 14: and carrying out fine adjustment on the fresh air cold water valve, the mixed cold water valve, the six-pipe unit compressor, the six-pipe unit balance pump, the heating steam valve and the humidifying steam valve according to the compared actual conditions.
2. An optimized control method for a combined air handling unit according to claim 1, characterized in that: step S121 is specifically as follows:
step S1211: closing the fresh air cold water valve, the mixed cold water valve and the six-pipe unit, and opening the heating steam valve and the humidifying steam valve;
step S1212: the opening degree of the heating steam valve is correspondingly adjusted according to the value of the heat load Q, and the opening degree of the humidifying steam valve is correspondingly adjusted according to the value of the humidity load W.
3. An optimized control method for a combined air handling unit according to claim 2, characterized in that: step S122 is specifically as follows:
step S1221: closing the fresh air cold water valve, closing the mixed cold water valve, closing the heating steam valve, closing the humidifying steam valve, and opening the six-pipe unit;
step S12211: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12212: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12213: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1222: if Tn is larger than or equal to Ta, starting a balance pump of the six-pipe unit, and adjusting the frequency of the balance pump of the six-pipe unit;
step S1223: if Tn is less than Ta, the balance pump of the six-pipe unit is closed, and the opening of the heating steam valve is adjusted.
4. An optimized control method for a combined air handling unit according to claim 3, characterized in that: step S123 specifically includes:
step S1231: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the humidifying steam valve, and opening the heating steam valve;
step S1232: and correspondingly adjusting the opening degree of the heating steam valve according to the numerical value of the heat load Q.
5. The optimized control method for combined air handling unit according to claim 4, characterized in that: step S124 is specifically as follows:
step S1241: closing the fresh air cold water valve, the six-pipe unit and the heating steam valve, and opening the mixed cold water valve and the humidifying steam valve;
step S1242: and adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q, and adjusting the opening of the humidifying steam valve according to the numerical value of the wet load W.
6. An optimized control method for a combined air handling unit according to claim 5, characterized in that: step S125 is specifically as follows:
step S1251: closing the fresh air cold water valve, the mixed cold water valve, the heating steam valve and the humidifying steam valve, and opening the six-pipe unit;
step S12511: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S12512: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S12513: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1252: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
7. The optimized control method for combined air handling unit according to claim 6, characterized in that: step S126 is specifically as follows:
step S1261: closing the fresh air cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve, and opening the mixing cold water valve;
step S1262: and correspondingly adjusting the opening of the mixed cold water valve according to the numerical value of the cold load Q.
8. The optimized control method for combined air handling unit according to claim 7, characterized in that: step S127 is specifically as follows:
step S1271: closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit and the heating steam valve, and opening the humidifying steam valve;
step S1272: and correspondingly adjusting the humidifying steam valve according to the value of the wet load W.
9. The optimized control method for combined air handling unit according to claim 8, characterized in that: step S128 is specifically as follows:
step S1281: if W is less than or equal to rho, 30% F (dj-dc) t, correspondingly adjusting the frequency of the compressor of the six-pipe unit according to the value of the wet load W;
step S1282: if rho 30% F (dj-dc) t < W is less than or equal to rho F (dm-dj) t + rho 30% F (dj-dc) t, correspondingly adjusting the opening of the mixed cold water valve according to the value of the wet load W on the premise that the six-pipe unit compressor operates at the maximum frequency;
step S1283: if W is more than rho F (dm-dj) t + rho 30% F (dj-dc) t, on the premise that the six-pipe unit compressor operates at the maximum frequency, the opening of the fresh air cold water valve is correspondingly adjusted according to the value of the wet load W, and the mixed cold water valve reaches the maximum opening;
step S1284: and correspondingly adjusting the frequency of the balance pump of the six-pipe unit according to the comparison value of Tn and Ta.
10. The optimized control method for combined air handling unit according to claim 9, characterized in that: step S129 is specifically as follows:
step S1291: and closing the fresh air cold water valve, the mixed cold water valve, the six-pipe unit, the heating steam valve and the humidifying steam valve.
CN202010896454.7A 2020-08-31 2020-08-31 Optimization control method for combined air treatment unit Active CN111895588B (en)

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