CN106529021B - A kind of air-conditioning system simulation method based on feature identification - Google Patents

A kind of air-conditioning system simulation method based on feature identification Download PDF

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CN106529021B
CN106529021B CN201610982619.6A CN201610982619A CN106529021B CN 106529021 B CN106529021 B CN 106529021B CN 201610982619 A CN201610982619 A CN 201610982619A CN 106529021 B CN106529021 B CN 106529021B
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cooler
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CN106529021A (en
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梁彩华
黄婷婷
凌善旭
张小松
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Southeast University
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • 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
    • 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
    • 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
    • F24F2110/40—Pressure, e.g. wind pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature

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Abstract

The present invention provides a kind of existing air-conditioning system simulation method based on feature identification, include: the actual measurement operation data according to existing air-conditioning system, solves the characteristic parameter of water cooler performance prediction model in air-conditioning system, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model and fluid supply pipe resistance model respectively using least square method；Each partial model for having acquired model parameter is subjected to simulation connection according to air-conditioning system actual motion process；Analogue simulation is carried out to air-conditioning system according to the correlated inputs parameter of simulation operating condition, exports the air-conditioning system running performance parameters.The air-conditioning system simulation method combines theory analysis, actual test with analogue simulation, can preferably characterize performance variation law of the air-conditioning system under different operating conditions, can be used as the basis of air-conditioning system overall performance simulation and forecast.

Description

A kind of air-conditioning system simulation method based on feature identification
Technical field
The invention belongs to air-conditioning system analogue simulation fields, are related to a kind of air-conditioning system analogue simulation based on feature identification Method.
Background technique
Traditional air-conditioning system Selection and Design is to run most preferably foundation under its declared working condition, and measured data shows sky The runing time of 80% or more unit is adjusted to run under 60% sub-load below, therefore for run most under declared working condition Good and design air-conditioning system needs to carry out optimization and energy saving and corresponding control to air-conditioning system to different load variations Strategy study, to avoid the reduction of running efficiency of system under sub-load.Based on air conditioner load changing rule, integrally transported from system The optimal angle of row compares and analyzes research to each optimal control for energy saving strategy of air-conditioning system, by analogue simulation means be compared with The method easily realized.It is specific due to each component of practical air-conditioning system when carrying out modeling and simulating to existing building air-conditioning system Structural parameters are difficult to obtain, and cause the accurately simulation carried out to foundation equipment specific structure parameter relatively difficult to achieve, so that conventional There is limitation in practical applications in modeling method.
Aiming at the problem that each component specific structure parameter of practical air conditioning system lacks, many scholars at home and abroad are proposed The method for suitably simplify to existing simulation model or measured data being combined to obtain experience and semiempirical formula establishes structure Device model under the conditions of parameter shortage.But pass through the simulation model accuracy for simplifying theoretical model or establishing based on empirical equation Lower and be difficult to promote in not homologous ray, the simulation model based on fitting formula is needed using magnanimity actual measurement operation data as base Plinth, and in practical existing air-conditioning system, the means for the measurement actual operation parameters that current conditions allow are limited.Therefore it needs to mention Under the conditions of structural parameters lack out, precision is higher, applicability is wider and required actual measurement parameter is less and in practical air-conditioning system The modeling method of acquisition can be facilitated.
Summary of the invention
Technical problem: the present invention propose it is a kind of under conditions of each component specific structure parameter of existing air-conditioning system lacks, Higher with precision, applicability is wider and required actual measurement parameter can facilitate the air-conditioning system of acquisition special in practical air-conditioning system Recognition methods is levied, and analogue simulation is carried out to air-conditioning system based on this feature recognition methods.
Technical solution: the air-conditioning system simulation method of the invention based on feature identification, comprising the following steps:
(1) according to the actual measurement operation data of existing air-conditioning system, solved respectively using least square method obtain it is following several The model parameter of model: water cooler performance prediction model, surface air cooler performance prediction model, cooling tower performance are pre- in air-conditioning system Model, water pump model, fluid supply pipe resistance model are surveyed, using obtained model parameter as each modular construction characteristic of characterization Characteristic parameter；
(2) according to the practical connection relationship of institute's analogue simulation air-conditioning system, by water cooler performance in the air-conditioning system Prediction model, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model, fluid supply pipe resistance model Carry out simulation connection；
(3) following system performance measure: water cooler evaporating temperature, water cooler condensation temperature, surface air cooler import is set Freezing temperature and cooling tower import coolant water temperature input the system performance measure and simulation duty parameter described together Each model of characteristic parameter has been determined in step (1), each running state parameter of air-conditioning system is calculated.
Further, water cooler performance prediction model includes evaporator model, condenser model, pressure in the method for the present invention Contracting machine model and throttle valve model:
A. the evaporator model is under variable water volume operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (3)
The evaporator model is in the case where becoming water temperature operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (8)
In formula, Qe1、Δte1The respectively heat exchange amount and heat transfer temperature difference of two-phase section；Qe2、Δte2The respectively heat exchange of overheated zone Amount and heat transfer temperature difference；mw,eFor chilled-water flow；cp,wFor the specific heat of water；mrFor refrigerant flow；A* eFor with evaporation structure and The related model parameter of dirtiness resistance；x1It is obtained for the water side coefficient of heat transfer empirical equation according to different structure form evaporator Constant coefficient；B* 1,eFor model parameter related with evaporation structure and dirtiness resistance；y1For according to different structure form evaporator The obtained constant coefficient of refrigerant side coefficient of heat transfer empirical equation；C* eFor model related with evaporation structure and dirtiness resistance Parameter；B* 2,eFor model parameter related with evaporation structure and dirtiness resistance；y2For according to different structure form evaporator The constant coefficient that refrigerant side coefficient of heat transfer empirical equation obtains；QeFor the total heat exchange amount of evaporator；twi,e, two,eRespectively chilled water Inlet temperature and outlet temperature；tw1,eFor two-phase section chilled water inlet temperature；hei, heoRespectively evaporator inlet enthalpy and outlet Enthalpy；teFor water cooler evaporating temperature；teoFor compressor air suction temperature, the i.e. refrigerant temperature of evaporator outlet；
B. the condenser model is under variable water volume operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (11)
The condenser model is in the case where becoming water temperature operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (16)
In formula, QcFor condenser heat exchange amount；mw,cFor cooling water flow；twi,c, two,cRespectively the cooling water of condenser into Mouth temperature and outlet temperature；hci, hcoThe respectively enthalpy of condenser inlet enthalpy and outlet；Δtc1, Δ tc2, Δ tc3Respectively Condenser crosses the heat transfer temperature difference of cold-zone, two-phase section and overheated zone；A* cFor it needs to be determined that condenser model parameter；x2For according to not The constant coefficient obtained with the water side coefficient of heat transfer empirical equation of structure type condenser；B* 1,cFor it needs to be determined that condenser model Parameter；y3The constant coefficient obtained for the refrigerant side coefficient of heat transfer empirical equation according to different structure form condenser；C* cTo need The condenser model parameter to be determined；B* 2,cFor it needs to be determined that condenser model parameter；y4It is cold according to different structure form The constant coefficient that the refrigerant side coefficient of heat transfer empirical equation of condenser obtains；B* 3,cFor it needs to be determined that condenser model parameter；y5 The constant coefficient obtained for the refrigerant side coefficient of heat transfer empirical equation according to different structure form condenser；tcIt is cold for water cooler Solidifying temperature；tcoFor refrigerant condensator outlet temperature；tw1,c, tw2,cRespectively two-phase section cooling water inlet temperature and outlet Temperature；tciFor compressor exhaust temperature；
C. the compressor model are as follows:
Vth=ψ Vth0 (22)
In formula, mrFor the mass flow of refrigerant；λ is gas transmission coefficient；VthFor compressor theory displacement；v1For compressor Inspiratory volume；ψ is water cooler rate of load condensate；Vth0For displacement theoretical under compressor declared working condition；TeoFor suction temperature；TciFor Delivery temperature；pcFor condensing pressure；peFor evaporating pressure；K is compression process polytropic exponent；PthFor compressor theoretical power (horse-power)；Pin For compressor actual power；ηeFor the electric energy efficiency of compressor；
D. throttle valve model are as follows:
hco=hei (26)
teo=te+Δte (27)
tco=tc-Δtc (28)
In formula, hcoFor the valve inlet enthalpy that throttles；heiFor the valve outlet enthalpy that throttles；ΔteFor the degree of superheat；ΔtcFor degree of supercooling；
The surface air cooler performance prediction model includes surface air cooler heat exchange amount model, surface air cooler heat conductive efficiency model, surface air cooler Contact coefficient model, surface air cooler heat transfer unit exponential model, heat capacity ratio model, outlet air parameter model；
The surface air cooler heat exchange amount model are as follows:
Qb=ma,b(hai,b-hao,b)=mw,bcp,w(two,b-twi,b) (29)
The surface air cooler heat conductive efficiency model are as follows:
The surface air cooler contact coefficient model are as follows: (31)
The surface air cooler heat transfer unit exponential model are as follows:
The heat capacity ratio model are as follows:
The outlet air parameter model, in dry cooling condition are as follows:
tgo,b=tgi,b-ε1,b(tgi,b-twi,b) (34)
The outlet air parameter model, in wet cooling condition are as follows:
tgo,b=tgi,b-ε2,b(tgi,b-tb) (36)
tso,b=tgo,b-(1-ε2,b)(tgi,b-tsi,b) (37)
The outlet air parameter model, in critical operating condition, when using above-mentioned dry cooling condition, outlet air parameter model when wet cooling condition ?；
In formula, QbFor surface air cooler heat exchange amount；ma,bFor air quality flow；hai,bFor air intake enthalpy；hao,bFor air Export enthalpy；mw,bFor water flow；twi,b, two,bRespectively surface air cooler inlet water temperature and exit water temperature；ε1,bIt conducts heat and imitates for surface air cooler Energy；tgi, tgoRespectively air intlet dry-bulb temperature and outlet dry-bulb temperature；γ is heat capacity ratio；NTU is surface air cooler heat transfer unit Number；ε2,bFor surface air cooler contact coefficient；tso,b, tsi,bRespectively air outlet slit wet-bulb temperature and import wet-bulb temperature；ao,bFor air The side coefficient of heat transfer；FbFor the total heat exchange area of surface air cooler；cp,aFor air specific heat；KbFor surface air cooler overall heat-transfer coefficient；tLiFor air into Mouth dew-point temperature；
The cooling tower performance prediction model, when air is under unsaturated state in cooling tower are as follows:
The cooling tower performance prediction model, in cooling tower air in the saturated condition when are as follows:
In formula, mw,tFor cooling tower water quality flow；Dz is cooling tower filler vertical direction infinitesimal length；βtFor cooling tower Mass tranfer coefficient；A is packing specific area；FzFor cooling tower filler cross-sectional area；Xs,wIt is the corresponding saturated air of water temperature containing wet Amount；X is air vapor mass component in cooling tower；Tw,tFor water temperature；Le is Lewis number；cp,vFor vapor specific heat at constant pressure； r0For the latent heat of vaporization of water；Ta,tFor air themperature in cooling tower；ma,tFor cooling tower air quality flow；Xs,aFor saturated air Water capacity；(βtaFZ)jFor the equivalence value in heat transfer process, Me is model parameter, mwi,tIndicate entrance water flow, HtIndicate filler Highly；
The water pump model are as follows:
Hp0=a0+a1V0+a2V0 2 (50)
Pin,p0=b0+b1V0+b2V0 2 (51)
In formula, V0、Hp0、Pin,p0Respectively pump is in revolving speed n0Under flow, lift and power, V1、Hp1、Pin,p1Respectively pump In revolving speed n1Under flow, lift and power；a0、a1、a2、b0、b1、b2For model parameter.
The fluid supply pipe resistance model are as follows:
In formula, HfFor equipment or pipe resistance, χiFor i-th section of pipeline frictional resistant coefficient, liFor i-th section of length of pipe, d For pipeline hydraulic diameter, ζjFor j-th of pipeline local resistance part resistance coefficient, V is conduit volume flow；For model parameter.
Further, in the step of the method for the present invention (1), the actual measurement operation data of existing air-conditioning system specifically: solve The model parameter of the water cooler performance prediction model, i.e. the solution model parameter of condenser, the model parameter of evaporator and When the model parameter of compressor, the measured data needed has compressor air suction temperature teo, suction pressure of compressor pe, compressor row Temperature degree tci, Compressor Discharge Pressure pc, water cooler rate of load condensate ψ, compressor horsepower Pin, cooling water flow mw,c, condenser into Saliva temperature twi,c, condensator outlet water temperature two,c, chilled-water flow mw,e, evaporator water temperature twi,e, evaporator outlet water temperature two,e；
When solving the model parameter of the surface air cooler performance prediction model, the measured data that needs are as follows: chilled-water flow mw,e, surface air cooler inlet water temperature twi,b, surface air cooler exit water temperature two,b, surface air cooler import dry-bulb temperature tgi,b, surface air cooler import it is wet Ball temperature tsi,b, surface air cooler export dry-bulb temperature tgo,b, surface air cooler export wet-bulb temperature tso,b；
When solving the model parameter of the cooling tower performance prediction model, the measured data that needs are as follows: cooling water flow mw,c, cooling tower inlet water temperature twi,t, cooling tower exit water temperature two,t, cooling tower import dry-bulb temperature tgi,t, cooling tower import it is wet Ball temperature tsi,t, cooling tower export dry-bulb temperature tgo,t, cooling tower export wet-bulb temperature tso,t；
When solving the model parameter of the water pump model, the measured data that needs are as follows: water pump is in revolving speed n0Under flow, raise Journey and power；
Solve the model parameter of the fluid supply pipe resistance model, the data for needing to survey are as follows: chilled-water flow mw,e, cooling water flow mw,c, pump head H1。
Further, in the method for the present invention step (1), water cooler in air-conditioning system is solved respectively using least square method Performance prediction model, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model and fluid supply pipe resistance When the characteristic parameter of model, guarantees the existence and uniqueness of Solution for System of Linear Equations using Cramer's rule, finally acquire feature The unique solution of parameter.
Further, each model of the air-conditioning system is carried out to the specific side of simulation connection in the method for the present invention step (2) Method are as follows: according to working media flow direction, by the working media state of each model arrival end, as the mould being connect with the arrival end The working media state of type outlet end, the working media include refrigerant, chilled water and cooling water；By chilled water pipeline resistance It is used as chilled water pump lift with the sum of equipment resistance, the sum of cooling water pipeline resistance and equipment resistance are raised as cooling water pump Journey.
Further, in the method for the present invention step (3), duty parameter is simulated specifically: water cooler mode input parameter Including water cooler rate of load condensate, chilled-water flow, cooling water flow；Surface air cooler performance prediction model input parameter includes: freezing Water flow, surface air cooler import air quantity, surface air cooler import dry-bulb temperature and wet-bulb temperature；Cooling tower performance prediction model inputs parameter It include: cooling water flow, cooling tower import air quantity, cooling tower import dry-bulb temperature and wet-bulb temperature.
Further, in the method for the present invention, the detailed process of step (3) are as follows:
1) surface air cooler import freezing temperature is set, it is done with chilled-water flow, surface air cooler import air quantity, surface air cooler import Wet-bulb temperature inputs surface air cooler performance prediction model together, carries out simulation calculating to surface air cooler outlet freezing temperature, the table is cold It is evaporator freezing temperature that device, which exports freezing temperature,；
Cooling tower import coolant water temperature is set, by itself and cooling water flow, cooling tower import air quantity, cooling tower import dry and wet Ball temperature inputs cooling tower performance prediction model together, carries out simulation calculating, the cooling tower to cooling tower outlet coolant water temperature Exporting coolant water temperature is condenser inlet coolant water temperature；
2) water cooler evaporating temperature and condensation temperature are set, it is inputted into compressor mould together with water cooler rate of load condensate Refrigerant flow, delivery temperature and compression electric power is calculated according to conventional compact polytropic process in type；
3) by compressor in the water cooler evaporating temperature and condensation temperature of setting, with chilled-water flow, the step 2) Evaporator freezing temperature obtained in refrigerant flow that model is calculated, the step 1), inputs evaporator together Model obtains evaporator refrigerant enthalpy and outlet refrigerant enthalpy, is calculated in evaporator in conjunction with refrigerant flow Refrigerant side heat exchange amount is equal to freezing heat transfer in water side using evaporator inner refrigerant side heat exchange amount according to heat conservation equation Evaporator outlet freezing temperature is calculated；According to heat transfer basic equation, calculated using evaporator total heat transfer and the coefficient of heat transfer The heat transfer temperature difference of refrigerant and chilled water in evaporator is obtained, the evaporator total heat transfer is equal to evaporator inner refrigerant side and changes Heat；
Compressor model in the water cooler condensation temperature of setting, with cooling water flow, the step 2) is calculated Delivery temperature, refrigerant flow, condenser inlet coolant water temperature obtained in the step 1), input condenser mould together Type obtains condenser inlet refrigerant enthalpy and outlet refrigerant enthalpy, is calculated in condenser and makes in conjunction with refrigerant flow Cryogen side heat exchange amount is equal to cooling water side heat exchange meter using condenser inner refrigerant side heat exchange amount according to heat conservation equation Calculation obtains condensator outlet coolant water temperature, according to heat transfer basic equation, is calculated using condenser total heat transfer and the coefficient of heat transfer The heat transfer temperature difference of refrigerant and cooling water into condenser, the condenser total heat transfer exchange heat equal to condenser inner refrigerant side Amount；
4) evaporator being calculated in evaporator freezing temperature, step 3) according to obtained in the step 1) goes out The heat transfer temperature difference of refrigerant and chilled water, is calculated the evaporating temperature of water cooler evaporator in mouth freezing temperature, evaporator；
According to the condensator outlet being calculated in condenser inlet coolant water temperature, step 3) obtained in the step 1) The heat transfer temperature difference of refrigerant and cooling water in coolant water temperature, condenser, is calculated the condensation temperature of water cooler condenser；
5) when following four groups of conditions are set up, then by evaporating temperature, condensation temperature, surface air cooler import freezing temperature, table It is total that cooler exports freezing temperature, condenser inlet coolant water temperature, condensator outlet coolant water temperature, compression electric power, evaporator Heat output and condenser total heat transfer are exported as system analog operational parameters, otherwise updated with the calculated value in every group of condition and The setting value compared, return step 1):
The surface air cooler import freezing temperature set in the step 1) and the evaporator being calculated in the step 3) go out Mouth freezing temperature is equal, the condenser being calculated in the cooling tower import coolant water temperature and step 3) set in the step 1) Export the evaporation temperature that coolant water temperature is equal, is calculated in the water cooler evaporating temperature and step 4) set in the step 3) Spend equal, the water cooler condensation temperature of the step 3) setting is equal with the condensation temperature being calculated in step 4).
Further, in the method for the present invention, water cooler performance prediction model, surface air cooler performance prediction model, cooling tower Performance prediction model, water pump model and fluid supply pipe resistance model are all based on lumped-parameter method, by existing air-conditioning system In each component unknown structure parameter carry out lump establish to obtain.
Further, in the method for the present invention, air-conditioning system is for separate unit water cooler central air conditioner system or by more cold water The air-conditioning system that unit, more water pumps and more set surface air cooler end/mixing-end equipments are constituted.
The present invention combines theory analysis with actual test, is being difficult to obtain each component specific structure parameter of air-conditioning system Under conditions of, it proposes the air-conditioning system characteristic recognition method of unknown structure lumping, according to measured data using minimum two Multiplication carries out feature identification to the unknown model parameters of each component of air-conditioning system, as the spy for characterizing each modular construction characteristic Parameter is levied, and is attached each partial model for having acquired characteristic parameter according to air-conditioning system actual motion process, passes through mould Quasi- operating condition correlated inputs parameter simulates air-conditioning system, has to the energy-efficient operation realized under unit full working scope important Theory and practical significance.
The utility model has the advantages that the present invention has the advantage that compared with existing air-conditioning system simulation method
Air-conditioning system equipment simulating method under the conditions of existing structure parameters default, it is main by simplifying theoretical model, base Simulation model is established in empirical equation or based on fitting formula, it is lower that there are precision, it is difficult to promote or emulate in not homologous ray Model needs the not strong problem of practical operation feasibility based on largely surveying operation data.
The present invention combines theory analysis, actual test with analogue simulation, is being difficult to obtain each portion of air-conditioning system first Under conditions of part specific structure parameter, propose to use the characteristic recognition method of unknown structure lumping according to measured data Least square method carries out feature identification to each component unknown model parameters of air-conditioning system, obtains the spy for characterizing each modular construction characteristic Parameter is levied, is attached each partial model for having acquired model parameter according still further to air-conditioning system actual motion process, each component The import and export state of model is similar with actual motion, finally by system performance measure and simulates operating condition using simulation method Parameter inputs each model that characteristic parameter has been determined together, and each running state parameter of air-conditioning system is calculated, can be effectively Unified consideration and accurate simulation are carried out for the links of air-conditioning system, to realize that the whole energy of air-conditioning system optimizes operation And the Evaluation on Energy Saving of system optimization scheme provides foundation.
Detailed description of the invention
Fig. 1 is that the present invention is the data measuring point value arrangement map for solving each component feature parameter in existing air-conditioning system and being arranged.
Fig. 2 is that the present invention is based on the air-conditioning system analogue simulation flow charts that feature identifies.
Specific embodiment
Below with reference to embodiment and Figure of description, the present invention is further illustrated.
Fig. 1 is the data measuring point value arrangement map for solving each component model parameters in existing air-conditioning system and being arranged.According to being based on The modeling principle of lumping solves water cooler performance prediction model, surface air cooler performance prediction model, cooling tower performance prediction The characteristic parameter of model, water pump model and fluid supply management group power model needs to combine related measured data, thus by figure Measuring point is arranged shown in 1: temperature and pressure sensor, real-time detection compressor air suction temperature are respectively arranged at compressor import and export Spend teo, suction pressure of compressor pe, compressor exhaust temperature tci, Compressor Discharge Pressure pc；Distinguish at condenser import and export Arrange temperature sensor, real-time detection condenser inlet water temperature twi,cWith exit water temperature two,c；Distinguish at evaporator import and export Arrange temperature sensor, real-time detection evaporator water temperature twi,eWith exit water temperature two,e；In the water outlet of condenser, evaporator Flow sensor, real-time detection cooling water flow m are respectively arranged on pipew,cWith chilled-water flow mw,e；At surface air cooler import and export It is respectively arranged temperature sensor, real-time detection surface air cooler inlet water temperature twi,bWith exit water temperature two,b；Measure surface air cooler import dry bulb Temperature tgi,b, surface air cooler import wet-bulb temperature tsi,b, surface air cooler export dry-bulb temperature tgo,b, surface air cooler export wet-bulb temperature tso,b； Temperature sensor, real-time detection cooling tower inlet water temperature t are respectively arranged at cooling tower import and exportwi,tWith exit water temperature two,t； Measure cooling tower import dry-bulb temperature tgi,t, cooling tower import wet-bulb temperature tsi,t, cooling tower export dry-bulb temperature tgo,t, it is cooling Tower exports wet-bulb temperature tso,t；Measure compressor horsepower Pin, chilled water pump power Pin,dpAnd cooling water pump power Pin,lp；It surveys Measure water cooler rate of load condensate ψ, chilled water pump revolving speed ndp, cooling water pump revolving speed nlp。
Fig. 2 is that air-conditioning system analogue simulation flow chart is identified based on feature, and the first step is based on lumped-parameter method, will both have time In adjusting system each component unknown structure parameter carry out lump, establish respectively water cooler performance prediction model in air-conditioning system, Surface air cooler performance prediction model, the performance prediction model of cooling tower, water pump model, fluid supply pipe resistance model, it is main to wrap It includes:
(1) water cooler performance prediction model:
A. evaporator model is under variable water volume operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (3)
Evaporator model is in the case where becoming water temperature operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (8)
In formula, Qe1、Δte1The respectively heat exchange amount and heat transfer temperature difference of two-phase section；Qe2、Δte2The respectively heat exchange of overheated zone Amount and heat transfer temperature difference；mw,eFor chilled-water flow；cp,wFor the specific heat of water；mrFor refrigerant flow；A* eFor with evaporation structure and The related model parameter of dirtiness resistance；x1It is obtained for the water side coefficient of heat transfer empirical equation according to different structure form evaporator Constant coefficient；B* 1,eFor model parameter related with evaporation structure and dirtiness resistance；y1For according to different structure form evaporator The obtained constant coefficient of refrigerant side coefficient of heat transfer empirical equation；C* eFor model related with evaporation structure and dirtiness resistance Parameter；B* 2,eFor model parameter related with evaporation structure and dirtiness resistance；y2For according to different structure form evaporator The constant coefficient that refrigerant side coefficient of heat transfer empirical equation obtains；QeFor the total heat exchange amount of evaporator；twi,e, two,eRespectively chilled water Inlet temperature and outlet temperature；tw1,eFor two-phase section chilled water inlet temperature；hei, heoRespectively evaporator inlet enthalpy and outlet Enthalpy；teFor water cooler evaporating temperature；teoFor compressor air suction temperature, i.e. evaporator outlet refrigerant temperature.
B. condenser model is under variable water volume operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (11)
Condenser model is in the case where becoming water temperature operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (16)
In formula, QcFor condenser heat exchange amount；mw,cFor cooling water flow；twi,c, two,cRespectively the cooling water of condenser into Mouth temperature and outlet temperature；hci, hcoThe respectively enthalpy of condenser inlet enthalpy and outlet；Δtc1, Δ tc2, Δ tc3Respectively Condenser crosses the heat transfer temperature difference of cold-zone, two-phase section and overheated zone；A* cFor it needs to be determined that condenser model parameter；x2For according to not The constant coefficient obtained with the water side coefficient of heat transfer empirical equation of structure type condenser；B* 1,cFor it needs to be determined that condenser model Parameter；y3The constant coefficient obtained for the refrigerant side coefficient of heat transfer empirical equation according to different structure form condenser；C* cTo need The condenser model parameter to be determined；B* 2,cFor it needs to be determined that condenser model parameter；y4It is cold according to different structure form The constant coefficient that the refrigerant side coefficient of heat transfer empirical equation of condenser obtains；B* 3,cFor it needs to be determined that condenser model parameter；y5 The constant coefficient obtained for the refrigerant side coefficient of heat transfer empirical equation according to different structure form condenser；tcIt is cold for water cooler Solidifying temperature；tcoFor refrigerant condensator outlet temperature；tw1,c, tw2,cRespectively two-phase section cooling water inlet temperature and outlet Temperature；tciFor compressor exhaust temperature.
C. compressor model are as follows:
Vth=ψ Vth0 (22)
In formula, mrFor the mass flow of refrigerant；λ is gas transmission coefficient；VthFor compressor theory displacement；v1For compressor Inspiratory volume；ψ is water cooler rate of load condensate, the compressor certain for structure type, and the theoretical displacement under declared working condition is Definite value determines the theoretical displacement under actual condition with the theoretical displacement ratio under declared working condition when carrying out energy adjustment Justice is water cooler rate of load condensate, is indicated with ψ；Run compressor for variable speed, ψ be compressor actual running speed with it is specified The ratio between revolving speed；For frequency-changeable compressor, ψ is the ratio between compressor actual motion frequency and rated frequency；Vth0It is specified for compressor Theoretical displacement under operating condition；TeoFor suction temperature；TciFor delivery temperature；pcFor condensing pressure；peFor evaporating pressure；K is compression Process polytropic exponent；PthFor compressor theoretical power (horse-power)；PinFor compressor actual power；ηeFor the electric energy efficiency of compressor；
Wherein, high speed, more thick stick compressors (n. >=720r/min, C=3%~4%) gas transmission coefficient lambda can be used following Empirical equation:
Electric energy efficiency ηeIt indicates are as follows:
ηe=ηi·ηm·ηd·ηmo
η in formulai、ηm、ηd、ηmoIt is indicated efficiency, friction efficiency, shaft coupling transmission efficiency and the motor effect of compressor respectively Rate.Usually take ηe=0.4~0.55.
D. throttle valve model are as follows:
hco=hei (26)
teo=te+Δte (27)
tco=tc-Δtc (28)
In formula, hcoFor the valve inlet enthalpy that throttles；heiFor the valve outlet enthalpy that throttles；ΔteFor the degree of superheat；ΔtcFor degree of supercooling；
(2) surface air cooler performance prediction model includes that following surface air cooler heat exchange amount model, surface air cooler heat conductive efficiency model, table are cold Device contact coefficient model, surface air cooler heat transfer unit exponential model, heat capacity ratio model, outlet air parameter model:
Surface air cooler heat exchange amount model:
Qb=ma,b(hai,b-hao,b)=mw,bcp,w(two,b-twi,b) (29)
Surface air cooler heat conductive efficiency model:
Surface air cooler contact coefficient model:
Surface air cooler heat transfer unit exponential model:
Heat capacity ratio model:
Outlet air parameter model, in dry cooling condition are as follows:
tgo,b=tgi,b-ε1,b(tgi,b-twi,b) (34)
Outlet air parameter model, in wet cooling condition are as follows:
tgo,b=tgi,b-ε2,b(tgi,b-tb) (36)
tso,b=tgo,b-(1-ε2,b)(tgi,b-tsi,b) (37)
Outlet air parameter model, in critical operating condition, when using above-mentioned dry cooling condition, outlet air parameter model when wet cooling condition it is equal It can；Critical operating condition is defined as herein, and leaving air temp is right up to the dew-point temperature of outlet air air.
In formula, QbFor surface air cooler heat exchange amount；ma,bFor air quality flow；hai,bFor air intake enthalpy；hao,bFor air Export enthalpy；mw,bFor water flow；twi,b, two,bRespectively surface air cooler inlet water temperature and exit water temperature；ε1,bIt conducts heat and imitates for surface air cooler Energy；tgi, tgoRespectively air intlet dry-bulb temperature and outlet dry-bulb temperature；γ is heat capacity ratio；NTU is surface air cooler heat transfer unit Number；ε2,bFor surface air cooler contact coefficient；tso,b, tsi,bRespectively air outlet slit wet-bulb temperature and import wet-bulb temperature；ao,bFor air The side coefficient of heat transfer；FbFor the total heat exchange area of surface air cooler；cp,aFor air specific heat；KbFor surface air cooler overall heat-transfer coefficient；tLiFor air into Mouth dew-point temperature；
(3) cooling tower performance prediction model, when air is under unsaturated state in cooling tower are as follows:
The cooling tower performance prediction model, in cooling tower air in the saturated condition when are as follows:
In formula, mw,tFor cooling tower water quality flow；Dz is cooling tower filler vertical direction infinitesimal length；βtFor cooling tower Mass tranfer coefficient；A is packing specific area；FzFor cooling tower filler cross-sectional area；Xs,wIt is the corresponding saturated air of water temperature containing wet Amount；X is air vapor mass component in cooling tower；Tw,tFor water temperature；Le is Lewis number；cp,vFor vapor specific heat at constant pressure； r0For the latent heat of vaporization of water；Ta,tFor air themperature in cooling tower；ma,tFor cooling tower air quality flow；Xs,aFor saturated air Water capacity；(βtaFZ)jFor the equivalence value in heat transfer process, Me is model parameter, mwi,tIndicate entrance water flow, HtIndicate filler Highly；
(4) water pump model are as follows:
Hp0=a0+a1V0+a2V0 2 (50)
Pin,p0=b0+b1V0+b2V0 2 (51)
In formula, V0、Hp0、Pin,p0Respectively pump is in revolving speed n0Under flow, lift and power, V1、Hp1、Pin,p1Respectively pump In revolving speed n1Under flow, lift and power；a0、a1、a2、b0、b1、b2For model parameter.
(5) fluid supply pipe resistance model are as follows:
In formula, HfFor equipment or pipe resistance, χiFor i-th section of pipeline frictional resistant coefficient, liFor i-th section of length of pipe, d For pipeline hydraulic diameter, ζjFor j-th of pipeline local resistance part resistance coefficient, V is conduit volume flow；For model parameter, Pump head under certain flow can be surveyed by air-conditioning system subtract equipment drag overall obtain itValue.
Second step is to solve the characteristic parameter of each component capabilities prediction model respectively according to measured data.It is hollow by Fig. 1 The data of correlation measuring point detection when adjusting system is run, are joined using the feature that least square method fitting characterizes each modular construction characteristic Number.
Third step is according to the practical connection relationship of institute's analogue simulation air-conditioning system, by water cooler in the air-conditioning system Performance prediction model, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model, fluid supply pipe resistance Model carries out simulation connection, specifically: compressor outlet connects condenser inlet when actual motion, compressor outlet system when simulation Cryogen state is condenser inlet refrigerant condition；Condensator outlet connection throttling valve inlet, when simulation, condense when actual motion It is throttling valve inlet refrigerant condition that device, which exports refrigerant condition,；The valve outlet that throttles when actual motion connects evaporator inlet, mould Throttling valve outlet refrigerant condition is evaporator inlet refrigerant condition when quasi-；Evaporator outlet connect compressor when actual motion Entrance, evaporator outlet refrigerant condition is suction port of compressor refrigerant condition when simulation；Freezing in evaporator when actual motion Water and refrigerant counterflow heat exchange, the chilled water flowed out from evaporator enters in surface air cooler to exchange heat with air inversion, and chilled water is from table It is entered back into evaporator after cooler outflow, evaporator outlet freezing water state is that surface air cooler entrance freezes water state, table when simulation Freezing water state in cooler outlet is that evaporator inlet freezes water state；Chilled water is equipped with when actual motion in chilled water pipeline Pump, the sum of chilled water pipeline resistance and equipment resistance are equal to chilled water pump lift when simulation；It is cooling in condenser when actual motion Water and refrigerant counterflow heat exchange, the cooling water flowed out from condenser enters in cooling tower to exchange heat with air inversion, and cooling water is from cold But it is entered back into condenser after tower outflow, the cooling water state of condensator outlet is cooling tower entrance cooling water state when simulation, cold But it is that condenser inlet freezes water state that tower, which exports cooling water state,；Cooling water is equipped with when actual motion in cooling water pipeline Pump, the sum of cooling water pipeline resistance and equipment resistance are equal to cooling water pump lift when simulation.
4th step is to set following system performance measure: water cooler evaporating temperature, water cooler condensation temperature, surface air cooler The system performance measure and simulation duty parameter are inputted exist together by import freezing temperature and cooling tower import coolant water temperature It is described Step 1: each model of characteristic parameter has been determined in two, each running state parameter of air-conditioning system is calculated.
Physical simulation process mainly comprises the steps that
1) surface air cooler import freezing temperature is set, it is done with chilled-water flow, surface air cooler import air quantity, surface air cooler import Wet-bulb temperature inputs surface air cooler performance prediction model together, carries out simulation meter to surface air cooler outlet freezing temperature according to the following formula It calculates, surface air cooler outlet freezing temperature is evaporator freezing temperature；
In dry cooling condition are as follows:
tgo,b=tgi,b-ε1,b(tgi,b-twi,b)
In wet cooling condition are as follows:
tgo,b=tgi,b-ε2,b(tgi,b-tb)
tso,b=tgo,b-(1-ε2,b)(tgi,b-tsi,b)
Cooling tower import coolant water temperature is set, by itself and cooling water flow, cooling tower import air quantity, cooling tower import dry and wet Ball temperature inputs cooling tower performance prediction model together, carries out simulation meter to cooling tower outlet coolant water temperature according to the following formula It calculates, cooling tower outlet coolant water temperature is condenser inlet coolant water temperature:
Air is under unsaturated state in cooling tower:
Air is in the saturated condition in cooling tower:
2) water cooler evaporating temperature and condensation temperature are set, it is inputted into compressor mould together with water cooler rate of load condensate Refrigerant flow, delivery temperature and compression electric power, specific calculating formula is calculated according to conventional compact polytropic process in type For；
Refrigerant flow:
Delivery temperature:
Compress electric power:
3) by the water cooler evaporating temperature and condensation temperature of setting, and obtained in chilled-water flow, the step 2) Surface air cooler obtained in refrigerant flow, the step 1) exports freezing temperature, inputs evaporator model together, obtains evaporator The heat exchange of evaporator inner refrigerant side can be calculated in conjunction with refrigerant flow in inlet refrigerant enthalpy and outlet refrigerant enthalpy Amount, calculating formula are as follows:
Qe=mr(heo-hei)
According to heat conservation equation, it is equal to freezing heat transfer in water side using evaporator inner refrigerant side heat exchange amount and is calculated Evaporator outlet freezing temperature:
two,e=twi,e-Qe/mw,ecp,w
According to heat transfer basic equation, refrigerant and chilled water is calculated using evaporator total heat transfer and the coefficient of heat transfer Heat transfer temperature difference, the evaporator total heat transfer are equal to evaporator inner refrigerant side heat exchange amount；
By the water cooler condensation temperature of setting, with delivery temperature obtained in cooling water flow, the step 2), refrigeration Cooling tower obtained in agent flux, the step 1) exports coolant water temperature, inputs condenser model together, obtains condenser inlet Refrigerant enthalpy and outlet refrigerant enthalpy, can be calculated condenser inner refrigerant side heat exchange amount in conjunction with refrigerant flow, count Formula are as follows:
Qc=mr(hci-hco)
According to heat conservation equation, it is equal to cooling water side heat exchange amount using condenser inner refrigerant side heat exchange amount and is calculated Condensator outlet coolant water temperature:
two,c=Qc/mw,ccp,w+twi,c
According to heat transfer basic equation, the heat transfer of refrigerant and cooling water is calculated in condenser total heat transfer and the coefficient of heat transfer The temperature difference, the condenser total heat transfer are equal to condenser inner refrigerant side heat exchange amount；
4) evaporator being calculated in evaporator freezing temperature, step 3) according to obtained in the step 1) goes out The heat transfer temperature difference of refrigerant and chilled water in mouth freezing temperature, evaporator, is calculated the evaporating temperature of water cooler evaporator:
According to the condenser being calculated in condenser inlet coolant water temperature obtained in the step 1), step 3) The heat transfer temperature difference of refrigerant and cooling water, is calculated the condensation temperature of water cooler condenser in outlet coolant water temperature, condenser Degree:
5) when following four groups of conditions are set up, then by evaporating temperature, condensation temperature, surface air cooler import freezing temperature, table It is total that cooler exports freezing temperature, condenser inlet coolant water temperature, condensator outlet coolant water temperature, compression electric power, evaporator Heat output and condenser total heat transfer are exported as system analog operational parameters, otherwise updated with the calculated value in every group of condition and The setting value compared, return step 1):
The surface air cooler import freezing temperature set in the step 1) and the evaporator being calculated in the step 3) go out Mouth freezing temperature is equal, the condenser being calculated in the cooling tower import coolant water temperature and step 3) set in the step 1) Export the evaporation temperature that coolant water temperature is equal, is calculated in the water cooler evaporating temperature and step 4) set in the step 3) Spend equal, the water cooler condensation temperature of the step 3) setting is equal with the condensation temperature being calculated in step 4).
Simulation process flow chart is as shown in Fig. 2, t in figurewi,bFor surface air cooler import freezing temperature, twi,tFor cooling tower import Coolant water temperature, two,eFor evaporator outlet freezing temperature, two,cFor condensator outlet coolant water temperature, te、tcWhat is respectively assumed is cold Water dispenser group evaporating temperature and condensation temperature, te'、tc' respectively simulate obtained evaporating temperature and condensation temperature.
Above-described embodiment is only the preferred embodiment of the present invention, it should be pointed out that: for the ordinary skill of the art For personnel, without departing from the principle of the present invention, several improvement and equivalent replacement can also be made, these are to the present invention Claim improve with the technical solution after equivalent replacement, each fall within protection scope of the present invention.

Claims (7)

1. a kind of air-conditioning system simulation method based on feature identification, which is characterized in that method includes the following steps:
(1) it according to the actual measurement operation data of existing air-conditioning system, is solved respectively using least square method and obtains following several models Model parameter: water cooler performance prediction model, surface air cooler performance prediction model, cooling tower performance prediction mould in air-conditioning system Type, water pump model, fluid supply pipe resistance model, using obtained model parameter as the spy for characterizing each modular construction characteristic Levy parameter；
In the step (1), water cooler performance prediction model include evaporator model, condenser model, compressor model and Throttle valve model:
A. the evaporator model is under variable water volume operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (3)
The evaporator model is in the case where becoming water temperature operating condition are as follows:
Qe=mw,ecp,w(twi,e-two,e)=mr(heo-hei) (8)
In formula, Qe1、Δte1The respectively heat exchange amount and heat transfer temperature difference of two-phase section；Qe2、Δte2Respectively the heat exchange amount of overheated zone and Heat transfer temperature difference；mw,eFor chilled-water flow；cp,wFor the specific heat of water；mrFor the mass flow of refrigerant；A* eFor with evaporation structure Model parameter related with dirtiness resistance；x1To be obtained according to the water side coefficient of heat transfer empirical equation of different structure form evaporator Constant coefficient；B* 1,eFor model parameter related with evaporation structure and dirtiness resistance；y1To be evaporated according to different structure form The constant coefficient that the refrigerant side coefficient of heat transfer empirical equation of device obtains；C* eFor mould related with evaporation structure and dirtiness resistance Shape parameter；B* 2,eFor model parameter related with evaporation structure and dirtiness resistance；y2For according to different structure form evaporator The obtained constant coefficient of refrigerant side coefficient of heat transfer empirical equation；QeFor the total heat exchange amount of evaporator；twi,e, two,eRespectively evaporate Device import chilled water temperature and evaporator outlet chilled water temperature；tw1,eFor two-phase section chilled water inlet temperature；hei, heoRespectively The enthalpy of evaporator inlet enthalpy and outlet；teFor water cooler evaporating temperature；teoFor compressor air suction temperature, i.e. evaporator goes out The refrigerant temperature of mouth；
B. the condenser model is under variable water volume operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (11)
The condenser model is in the case where becoming water temperature operating condition are as follows:
Qc=mw,ccp,w(two,c-twi,c)=mr(hci-hco) (16)
In formula, QcFor condenser heat exchange amount；mw,cFor cooling water flow；twi,c, two,cThe respectively cooling water inlet temperature of condenser Degree and outlet temperature；hci, hcoThe respectively enthalpy of condenser inlet enthalpy and outlet；Δtc1, Δ tc2, Δ tc3Respectively condense Device crosses the heat transfer temperature difference of cold-zone, two-phase section and overheated zone；A* cFor it needs to be determined that condenser model parameter；x2For according to different knots The constant coefficient that the water side coefficient of heat transfer empirical equation of configuration formula condenser obtains；B* 1,cFor it needs to be determined that condenser model ginseng Number；y3The constant coefficient obtained for the refrigerant side coefficient of heat transfer empirical equation according to different structure form condenser；C* cTo need Determining condenser model parameter；B* 2,cFor it needs to be determined that condenser model parameter；y4To be condensed according to different structure form The constant coefficient that the refrigerant side coefficient of heat transfer empirical equation of device obtains；B* 3,cFor it needs to be determined that condenser model parameter；y5For The constant coefficient obtained according to the refrigerant side coefficient of heat transfer empirical equation of different structure form condenser；tcFor water cooler condensation Temperature；tcoFor refrigerant condensator outlet temperature；tw1,c, tw2,cRespectively two-phase section cooling water inlet temperature and outlet temperature Degree；tciFor compressor exhaust temperature；
C. the compressor model are as follows:
Vth=ψ Vth0 (22)
In formula, mrFor the mass flow of refrigerant；λ is gas transmission coefficient；VthFor compressor theory displacement；v1For compressor air suction Specific volume；ψ is water cooler rate of load condensate；Vth0For displacement theoretical under compressor declared working condition；TeoFor suction temperature；TciFor exhaust Temperature；pcFor Compressor Discharge Pressure；peFor suction pressure of compressor；K is compression process polytropic exponent；PthFor compressor theory Power；PinFor compressor actual power；ηeFor the electric energy efficiency of compressor；
D. throttle valve model are as follows:
hco=hei (26)
teo=te+△te (27)
tco=tc-△tc (28)
Δ t in formulaeFor the degree of superheat；ΔtcFor degree of supercooling；
The surface air cooler performance prediction model includes surface air cooler heat exchange amount model, surface air cooler heat conductive efficiency model, surface air cooler contact Modulus Model, surface air cooler heat transfer unit exponential model, heat capacity ratio model, outlet air parameter model；
The surface air cooler heat exchange amount model are as follows:
Qb=ma,b(hai,b-hao,b)=mw,bcp,w(two,b-twi,b) (29)
The surface air cooler heat conductive efficiency model are as follows:
The surface air cooler contact coefficient model are as follows:
The surface air cooler heat transfer unit exponential model are as follows:
The heat capacity ratio model are as follows:
The outlet air parameter model, in dry cooling condition are as follows:
tgo,b=tgi,b-ε1,b(tgi,b-twi,b) (34)
The outlet air parameter model, in wet cooling condition are as follows:
tgo,b=tgi,b-ε2,b(tgi,b-tb) (36)
tso,b=tgo,b-(1-ε2,b)(tgi,b-tsi,b) (37)
The outlet air parameter model, in critical operating condition, when using above-mentioned dry cooling condition, outlet air parameter model when wet cooling condition it is equal It can；
In formula, QbFor surface air cooler heat exchange amount；ma,bFor air quality flow；hai,bFor air intake enthalpy；hao,bFor air outlet slit Enthalpy；mw,bFor water flow；twi,b, two,bRespectively surface air cooler inlet water temperature and exit water temperature；ε1,bFor surface air cooler heat conductive efficiency； tgi,b, tgo,bRespectively surface air cooler import import dry-bulb temperature and surface air cooler import export dry-bulb temperature；γ is heat capacity ratio；NTU is Surface air cooler number of transfer units；ε2,bFor surface air cooler contact coefficient；tso,b, tsi,bRespectively air outlet slit wet-bulb temperature and import wet bulb Temperature；ao,bFor the air side coefficient of heat transfer；FbFor the total heat exchange area of surface air cooler；cp,aFor air specific heat；KbIt always conducts heat for surface air cooler and is Number；tLiFor air intlet dew-point temperature；
The cooling tower performance prediction model, when air is under unsaturated state in cooling tower are as follows:
The cooling tower performance prediction model, in cooling tower air in the saturated condition when are as follows:
In formula, mw,tFor cooling tower water quality flow；Dz is cooling tower filler vertical direction infinitesimal length；βtFor cooling tower mass transfer system Number；A is packing specific area；FzFor cooling tower filler cross-sectional area；Xs,wFor the corresponding saturated air water capacity of water temperature；X is cold But air vapor mass component in tower；Tw,tFor water temperature；Le is Lewis number；cp,vFor vapor specific heat at constant pressure；r0For water The latent heat of vaporization；Ta,tFor air themperature in cooling tower；ma,tFor cooling tower air quality flow；Xs,aFor saturated air water capacity； (βtaFZ)jFor the equivalence value in heat transfer process, Me is model parameter, mwi,tIndicate entrance water flow, HtIndicate packed height；
The water pump model are as follows:
Hp0=a0+a1V0+a2V0 2 (50)
Pin,p0=b0+b1V0+b2V0 2 (51)
In formula, V0、Hp0、Pin,p0Respectively pump is in revolving speed n0Under flow, lift and power, V1、Hp1、Pin,p1Respectively pump is turning Fast n1Under flow, lift and power；a0、a1、a2、b0、b1、b2For model parameter；
The fluid supply pipe resistance model are as follows:
In formula, HfFor equipment or pipe resistance, χiFor i-th section of pipeline frictional resistant coefficient, liFor i-th section of length of pipe, d is pipe Road hydraulic diameter, ζjFor j-th of pipeline local resistance part resistance coefficient, V is conduit volume flow；For model parameter, g attaches most importance to Power acceleration；
The actual measurement operation data of the existing air-conditioning system specifically: solve the model ginseng of the water cooler performance prediction model When number, the i.e. model parameter of the solution model parameter of condenser, the model parameter of evaporator and compressor, the measured data that needs There is compressor air suction temperature teo, suction pressure of compressor pe, compressor exhaust temperature tci, Compressor Discharge Pressure pc, cooling-water machine Group rate of load condensate ψ, compressor actual power Pin, cooling water flow mw,c, condenser cooling water inlet water temperature twi,c, condenser Cooling water outlet water temperature two,c, chilled-water flow mw,e, evaporator chilled water temperature twi,e, evaporator outlet chilled water temperature two,e；
When solving the model parameter of the surface air cooler performance prediction model, the measured data that needs are as follows: chilled-water flow mw,e, table Cooler inlet water temperature twi,b, surface air cooler exit water temperature two,b, surface air cooler import dry-bulb temperature tgi,b, surface air cooler import wet-bulb temperature tsi,b, surface air cooler export dry-bulb temperature tgo,b, surface air cooler export wet-bulb temperature tso,b；
When solving the model parameter of the cooling tower performance prediction model, the measured data that needs are as follows: cooling water flow mw,c, it is cold But tower inlet water temperature twi,t, cooling tower exit water temperature two,t, cooling tower import dry-bulb temperature tgi,t, cooling tower import wet-bulb temperature tsi,t, cooling tower export dry-bulb temperature tgo,t, cooling tower export wet-bulb temperature tso,t；
When solving the model parameter of the water pump model, the measured data that needs are as follows: water pump is in revolving speed n0Under flow, lift and Power；
Solve the model parameter of the fluid supply pipe resistance model, the data for needing to survey are as follows: chilled-water flow mw,e, it is cold But water flow mw,c, pump head H1；
(2) according to the practical connection relationship of institute's analogue simulation air-conditioning system, by water cooler performance prediction in the air-conditioning system Model, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model, fluid supply pipe resistance model carry out Simulation connection；
(3) following system performance measure: water cooler evaporating temperature, water cooler condensation temperature, surface air cooler import freezing is set Water temperature and cooling tower import coolant water temperature input the system performance measure and simulation duty parameter in the step together (1) each model of characteristic parameter has been determined in, each running state parameter of air-conditioning system is calculated.
2. a kind of air-conditioning system simulation method based on feature identification according to claim 1, which is characterized in that institute It states in step (1), it is pre- to solve water cooler performance prediction model in air-conditioning system, surface air cooler performance respectively using least square method When surveying the characteristic parameter of model, cooling tower performance prediction model, water pump model and fluid supply pipe resistance model, a gram Lay is used Nurse rule guarantees the existence and uniqueness of Solution for System of Linear Equations, finally acquires the unique solution of characteristic parameter.
3. a kind of air-conditioning system simulation method based on feature identification according to claim 1 or 2, feature exist In simulation connection in the step (2) method particularly includes: according to working media flow direction, by the work of each model arrival end Make medium state, as the working media state at the mold exit end connecting with the arrival end, the working media includes refrigeration Agent, chilled water and cooling water；The sum of chilled water pipeline resistance and equipment resistance are regard as chilled water pump lift, by cooling water pipeline The sum of resistance and equipment resistance are used as cooling water pump lift.
4. a kind of air-conditioning system simulation method based on feature identification according to claim 1 or 2, feature exist In in the step (3), simulating duty parameter specifically: water cooler mode input parameter includes water cooler rate of load condensate, cold Freeze water flow, cooling water flow；Surface air cooler performance prediction model input parameter include: chilled-water flow, surface air cooler import air quantity, Surface air cooler import dry-bulb temperature and wet-bulb temperature；It includes: cooling water flow, cooling tower that cooling tower performance prediction model, which inputs parameter, Import air quantity, cooling tower import dry-bulb temperature and wet-bulb temperature.
5. a kind of air-conditioning system simulation method based on feature identification according to claim 4, which is characterized in that institute State the detailed process of step (3) are as follows:
1) surface air cooler import freezing temperature is set, by itself and chilled-water flow, surface air cooler import air quantity, surface air cooler import wet and dry bulb Temperature inputs surface air cooler performance prediction model together, carries out simulation calculating to surface air cooler outlet freezing temperature, the surface air cooler goes out Mouth freezing temperature is evaporator freezing temperature；
Cooling tower import coolant water temperature is set, by itself and cooling water flow, cooling tower import air quantity, cooling tower import wet and dry bulb temperature Degree inputs cooling tower performance prediction model together, carries out simulation calculating, the cooling tower outlet to cooling tower outlet coolant water temperature Coolant water temperature is condenser inlet coolant water temperature；
2) water cooler evaporating temperature and condensation temperature are set, it is inputted into compressor model together with water cooler rate of load condensate, Refrigerant flow, delivery temperature and compression electric power is calculated according to conventional compact polytropic process；
3) by compressor model in the water cooler evaporating temperature and condensation temperature of setting, with chilled-water flow, the step 2) Evaporator freezing temperature obtained in the refrigerant flow that is calculated, the step 1), inputs evaporator model together, Evaporator refrigerant enthalpy and outlet refrigerant enthalpy are obtained, evaporator inner refrigerant is calculated in conjunction with refrigerant flow Side heat exchange amount is equal to freezing heat transfer in water side using evaporator inner refrigerant side heat exchange amount and calculates according to heat conservation equation To evaporator outlet freezing temperature；According to heat transfer basic equation, steaming is calculated using evaporator total heat transfer and the coefficient of heat transfer The heat transfer temperature difference of refrigerant and chilled water in device is sent out, the evaporator total heat transfer is equal to evaporator inner refrigerant side heat exchange amount；
By the row that compressor model is calculated in the water cooler condensation temperature of setting, with cooling water flow, the step 2) Temperature degree, refrigerant flow, condenser inlet coolant water temperature obtained in the step 1), input condenser model together, obtain To condenser inlet refrigerant enthalpy and outlet refrigerant enthalpy, condenser inner refrigerant side is calculated in conjunction with refrigerant flow Heat exchange amount is equal to cooling water side heat exchange amount using condenser inner refrigerant side heat exchange amount and is calculated according to heat conservation equation Condensation is calculated using condenser total heat transfer and the coefficient of heat transfer according to heat transfer basic equation in condensator outlet coolant water temperature The heat transfer temperature difference of refrigerant and cooling water in device, the condenser total heat transfer are equal to condenser inner refrigerant side heat exchange amount；
4) evaporator outlet being calculated in evaporator freezing temperature, step 3) according to obtained in the step 1) is cold The heat transfer temperature difference of refrigerant and chilled water, is calculated the evaporating temperature of water cooler evaporator in jelly water temperature, evaporator；
It is cooling according to the condensator outlet being calculated in condenser inlet coolant water temperature, step 3) obtained in the step 1) The heat transfer temperature difference of refrigerant and cooling water in water temperature, condenser, is calculated the condensation temperature of water cooler condenser；
5) when following four groups of conditions are set up, then by evaporating temperature, condensation temperature, surface air cooler import freezing temperature, surface air cooler Outlet freezing temperature, condenser inlet coolant water temperature, condensator outlet coolant water temperature, compression electric power, evaporator always conduct heat Amount and condenser total heat transfer as system analog operational parameters export, otherwise in every group of condition calculated value update and the ratio between Compared with setting value, return step 1):
The surface air cooler import freezing temperature set in the step 1) and the evaporator outlet being calculated in the step 3) are cold Freeze the condensator outlet that water temperature is equal, is calculated in the cooling tower import coolant water temperature and step 3) set in the step 1) Coolant water temperature is equal, the water cooler evaporating temperature set in the step 3) and the evaporating temperature phase being calculated in step 4) Deng the water cooler condensation temperature of the step 3) setting is equal with the condensation temperature being calculated in step 4).
6. a kind of air-conditioning system simulation method based on feature identification according to claim 1 or 2, feature exist In, the water cooler performance prediction model, surface air cooler performance prediction model, cooling tower performance prediction model, water pump model and Fluid supply pipe resistance model is all based on lumped-parameter method, by the unknown structure parameter of component each in existing air-conditioning system into Row lump establishes to obtain.
7. a kind of air-conditioning system simulation method based on feature identification according to claim 1 or 2, feature exist In the air-conditioning system is cold for separate unit water cooler central air conditioner system or by more water coolers, more water pumps and more set tables The air-conditioning system that device end/mixing-end equipment is constituted.
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