CN117648885A - Optimization method of dehumidification scheme of pumped storage power station factory building based on numerical simulation - Google Patents
Optimization method of dehumidification scheme of pumped storage power station factory building based on numerical simulation Download PDFInfo
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Abstract
The invention provides an optimization method of a water-pumped storage power station plant dehumidification scheme based on numerical simulation, which comprises the following steps: establishing a ventilation tunnel fluid mechanics model; performing simulation on the fluid in the ventilation tunnel, and outputting simulated air parameters of the outlet of the ventilation tunnel; and determining a dehumidification scheme adopted by the vent hole outlet according to the vent hole outlet air parameters. According to the invention, the change of the flow field characteristic parameters is obtained by simulating the air flow in the ventilation hole of the pumped storage power station, so that the air parameters of the outlet of the ventilation hole are obtained, and the minimum number of the dehumidifier arrangements meeting the temperature and humidity requirements in the factory is obtained by influencing the air parameters in the factory by the number of the dehumidifier, so that the energy saving maximization is realized. The invention has accurate simulation process, high simulation speed and high simulation result precision, and can realize that the optimal number of the dehumidifier arrangements can be obtained in real time according to the inlet parameters of the ventilating holes, thereby starting the dehumidifiers with corresponding numbers and ensuring that the temperature and the humidity in the factory building meet the requirements.
Description
Technical Field
The invention belongs to the technical field of ventilation and dehumidification of pumped storage power stations, and particularly relates to an optimization method of a dehumidification scheme of a pumped storage power station plant based on numerical simulation.
Background
In order to realize low-carbon energy development, auxiliary support of energy storage technology is urgently needed in an electric power system to promote the system to absorb new energy level, so that the traditional fossil energy consumption is reduced, and the carbon emission is reduced.
The pumped storage technology has the advantages of short starting time, high load increasing and decreasing speed, flexible operation mode, capability of bearing various functions such as peak regulation, frequency modulation and the like, almost no pollution to the environment and the like, and stands out in various energy storage schemes.
The pumped storage power station plant is arranged underground, and the inlet of the plant is communicated with the air on the ground through a ventilation hole. That is, the above-ground air flows through the ventilation hole and then flows into the factory building. Because more electromechanical devices are arranged in the factory building, the requirements on the environmental temperature and humidity are higher, and how to enable the environmental temperature and humidity in the factory building to meet the requirements on the premise of maximizing energy conservation is an important problem to be solved at present.
Disclosure of Invention
Aiming at the defects existing in the prior art, the invention provides an optimization method of a water pumping and energy storage power station factory building dehumidification scheme based on numerical simulation, which can effectively solve the problems.
The technical scheme adopted by the invention is as follows:
the invention provides an optimization method of a water-pumped storage power station plant dehumidification scheme based on numerical simulation, which comprises the following steps:
step 1, establishing a fluid mechanics model of a ventilation hole, wherein the fluid mechanics model comprises a three-dimensional model of the ventilation hole, an air supply boundary of the ventilation hole, a wall temperature boundary of the ventilation hole and a flow model;
wherein the ventilation hole air supply boundary comprises the air dry bulb temperature t at the inlet of the ventilation hole T0 Relative humidity correction for ventilation tunnel inlet airThe inlet wind speed v of the ventilation hole;
the ventilation hole wall temperature boundary comprises a ventilation hole wall temperature boundary and a ventilation hole simulation wall moisture dispersion amount; wherein, ventilation hole wall temperature boundary refers to: setting the value of the ground depth Y to obtain the wall temperature t corresponding to each ground depth Y in the ventilation hole, thereby forming a ventilation hole wall temperature boundary;
step 2, executing the flow model in the three-dimensional model of the ventilation hole by taking the air supply boundary of the ventilation hole and the temperature boundary of the wall surface of the ventilation hole determined in the step 1 as boundary conditions, and carrying out simulation on fluid in the ventilation hole by the flow model to output simulated air parameters of an outlet of the ventilation hole and a temperature and humidity cloud picture of a section of the ventilation hole; wherein the ventilation hole outlet air parameters comprise the ventilation hole outlet air temperature t T2 Relative humidity of air at vent hole outletMoisture content d of air at outlet of ventilation hole T2 Enthalpy of air at vent outlet i T2 ；
Step 3, detecting the precision of the fluid mechanics model of the ventilation tunnel according to the temperature and humidity cloud picture of the section of the ventilation tunnel, and executing step 4 if the detection passes; if the detection does not pass, returning to the step 2, and correcting the fluid mechanics model of the ventilation tunnel;
and step 4, determining a dehumidification scheme adopted by the vent outlet according to the vent outlet air parameters:
step 4.1, giving the air quantity G of the factory building 1 ；
Step 4.2, determining parameters of the dehumidifier, including: rated air quantity G of single dehumidifier c The dehumidification efficiency parameter gamma of the single dehumidifier, the input power N of the single dehumidifier and the rated dehumidification capacity W of the single dehumidifier c ；
Step 4.3, determining an initial value of the number n of dehumidifier units required to be arranged at the outlet of the ventilating hole;
step 4.4, employing equation Q 1 ＝γ*W c Obtaining the actual refrigerating capacity Q of a single dehumidifier 1 The method comprises the steps of carrying out a first treatment on the surface of the Using formula Q 2 ＝Q 1 +nN, the total heat dissipation Q of n dehumidifier is obtained 2 ；
Step 4.5, obtaining the outlet air moisture content d of the n dehumidifiers by adopting the following formula c ：
Step 4.6, according to the outlet air moisture content d of the n dehumidifiers c Obtaining the corresponding saturated air dry bulb temperature t by searching the enthalpy-humidity diagram c0 ；
The temperature t of the dry bulb of the outlet air of the dehumidifier is obtained by adopting the following steps c The temperature of the air dry bulb at the outlet of the dehumidifier after the heat of the dehumidifier is increased;
step 4.7, according to the temperature t of the dry bulb of the outlet air of the dehumidifier c Moisture content d of outlet air c Searching an enthalpy-humidity diagram to obtain the corresponding enthalpy i of the outlet air of the dehumidifier c ；
Step 4.8, discharging a part of air at the outlet of the ventilating hole after being treated by n dehumidifiers; the other part is not processed by n dehumidifier; air not treated by dehumidifier and nThe air discharged after being processed by the dehumidifier forms mixed air, and the mixed air is conveyed into a factory building; the moisture content d of the mixed wind is obtained by the following formula H And enthalpy i of mixed wind H ：
G 0 ＝G 1 -nG c
Wherein:
G 1 the air quantity of the factory building; g 0 The air quantity is the air quantity which is not processed by the dehumidifier;
step 4.9, according to the moisture content d of the mixed wind H And enthalpy i of mixed wind H Obtaining the dry bulb temperature t of the mixed air by searching the enthalpy-humidity diagram H And the relative humidity of the mixed wind
Step 4.10, judging the dry bulb temperature t of the mixed air H Whether is greater than the lower limit value t of the dry bulb temperature of the factory building x At the same time, the relative humidity of the mixed windWhether is lower than the upper limit value of the relative humidity of the factory building>If the number of the dehumidifier is satisfied, the number n of the dehumidifier at the moment is the number of the finally determined dehumidifier arranged at the outlet of the ventilating hole, and a dehumidification scheme is obtained; if not, the number n of the dehumidifier is increased by 1, and the process returns to the step 4.4 for cyclic execution.
Preferably, in step 1, the method for establishing the three-dimensional model of the ventilation hole includes: obtaining a ventilation hole structure parameter; establishing a three-dimensional model of the ventilation tunnel according to the ventilation tunnel structure parameters; the ventilation hole structure parameters comprise a ventilation hole inlet section area A, a ventilation hole wall surface area B and a ventilation hole total length L.
Preferably, in step 1, the ventilation hole inlet air corrects the relative humidityThe determining method of (1) comprises the following steps:
step A1, obtaining the moisture content d of air at the inlet of the ventilation hole by adopting the following formula T0 ：
Wherein:
air relative humidity is input to the ventilation hole; p (P) sb The saturated vapor pressure of the air at the inlet of the ventilation hole; atm is standard atmospheric pressure;
step A2, obtaining the total moisture dispersion w of the ventilation hole by adopting the following steps b ：
w b ＝w*B
Wherein:
w is the moisture dispersion of the wall surface of the ventilation hole;
b is the wall area of the ventilation hole;
step A3, obtaining the corrected moisture content d of the inlet air of the ventilating hole by adopting the following steps T1 ：
Wherein: g is the air quantity of the ventilation hole;
step A4, according to the temperature t of the dry ball of the inlet air of the ventilating hole T0 And ventilation hole inlet air correction moisture content d T1 Searching the enthalpy-humidity diagram to obtain the corresponding corrected relative humidity of the inlet air of the ventilating hole
Preferably, in step 1, the method for determining the inlet wind speed v of the ventilation hole is as follows: using the formulaAnd obtaining the inlet wind speed v of the ventilating hole.
Preferably, in step 1, the following formula is adopted to obtain the wall surface temperature Y corresponding to each buried depth Y of the ventilation hole:
wherein:
t dy is the surface temperature; θ dy The temperature amplitude of the ground surface is the annual amplitude; t is t f Is the additional value of the ground temperature; w (w) y Is the temperature annual amplitude frequency; y is the depth of the ground; a, a y Is the temperature conductivity of the formation material.
Preferably, in step 2, when the flow model simulates the fluid in the ventilation hole, a section is selected from the three-dimensional model of the ventilation hole at intervals of a set distance, each section has a section average temperature, and the three-dimensional model of the ventilation hole is structured into a grid, so that the simulation is performed.
The optimization method of the water-pumped storage power station factory building dehumidification scheme based on numerical simulation has the following advantages:
the invention provides an optimization method of a dehumidifying scheme of a pumped storage power station plant based on numerical simulation, which is characterized in that the change of flow field characteristic parameters is obtained by simulating the air flow in a ventilation hole of the pumped storage power station, so that the air parameters of an outlet of the ventilation hole are obtained, and the minimum number of dehumidifier arrangements meeting the temperature and humidity requirements in the plant is obtained by the influence of the number of dehumidifiers on the air parameters in the plant, so that the energy conservation is maximized. The invention has accurate simulation process, high simulation speed and high simulation result precision, and can realize that the optimal number of the dehumidifier arrangements can be obtained in real time according to the inlet parameters of the ventilating holes, thereby starting the dehumidifiers with corresponding numbers and ensuring that the temperature and the humidity in the factory building meet the requirements.
Drawings
FIG. 1 is a flow diagram of an optimization method of a pumped storage power station plant dehumidification scheme based on numerical simulation;
FIG. 2 is a graph comparing simulated and measured temperatures of a fluid mechanics model of a ventilation tunnel provided by the present invention.
Detailed Description
In order to make the technical problems, technical schemes and beneficial effects solved by the invention more clear, the invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
The invention provides an optimization method of a dehumidifying scheme of a pumped storage power station plant based on numerical simulation, which is characterized in that the change of flow field characteristic parameters is obtained by simulating the air flow in a ventilation hole of the pumped storage power station, so that the air parameters of an outlet of the ventilation hole are obtained, and the minimum number of dehumidifier arrangements meeting the temperature and humidity requirements in the plant is obtained by the influence of the number of dehumidifiers on the air parameters in the plant, so that the energy conservation is maximized. The invention has accurate simulation process, high simulation speed and high simulation result precision, and can realize that the optimal number of the dehumidifier arrangements can be obtained in real time according to the inlet parameters of the ventilating holes, thereby starting the dehumidifiers with corresponding numbers and ensuring that the temperature and the humidity in the factory building meet the requirements.
The invention provides an optimization method of a water-pumped storage power station plant dehumidification scheme based on numerical simulation, which refers to fig. 1 and comprises the following steps:
step 1, establishing a fluid mechanics model of a ventilation hole, wherein the fluid mechanics model comprises a three-dimensional model of the ventilation hole, an air supply boundary of the ventilation hole, a wall temperature boundary of the ventilation hole and a flow model;
wherein the ventilation hole air supply boundary comprises the air dry bulb temperature t at the inlet of the ventilation hole T0 Relative humidity correction for ventilation tunnel inlet airThe inlet wind speed v of the ventilation hole;
the ventilation hole wall temperature boundary comprises a ventilation hole wall temperature boundary and a ventilation hole simulation wall moisture dispersion amount; wherein, ventilation hole wall temperature boundary refers to: setting the value of the ground depth Y to obtain the wall temperature t corresponding to each ground depth Y in the ventilation hole, thereby forming a ventilation hole wall temperature boundary;
in this step, the method for establishing the three-dimensional model of the ventilation tunnel comprises the following steps: obtaining a ventilation hole structure parameter; establishing a three-dimensional model of the ventilation tunnel according to the ventilation tunnel structure parameters; the ventilation hole structure parameters comprise a ventilation hole inlet section area A, a ventilation hole wall surface area B and a ventilation hole total length L.
In this step, the relative humidity of the ventilation hole inlet air is correctedThe determining method of (1) comprises the following steps:
step A1, obtaining the moisture content d of air at the inlet of the ventilation hole by adopting the following formula T0 ：
Wherein:
air relative humidity is input to the ventilation hole; p (P) sB The saturated vapor pressure of the air at the inlet of the ventilation hole; atm is standard atmospheric pressure;
step A2, obtaining the total moisture dispersion w of the ventilation hole by adopting the following steps b ：
w b ＝w*B
Wherein:
w is the moisture dispersion of the wall surface of the ventilation hole;
b is the wall area of the ventilation hole;
step A3, obtaining the corrected moisture content d of the inlet air of the ventilating hole by adopting the following steps T1 ：
Wherein: g is the air quantity of the ventilation hole;
step A4, according to the temperature t of the dry ball of the inlet air of the ventilating hole T0 And ventilation hole inlet air correction moisture content d T1 Searching the enthalpy-humidity diagram to obtain the corresponding corrected relative humidity of the inlet air of the ventilating hole
In the step, the method for determining the inlet wind speed v of the ventilation tunnel comprises the following steps: using the formulaAnd obtaining the inlet wind speed c of the ventilating hole.
In the step, the wall surface temperature t corresponding to each buried depth Y of the ventilation hole is obtained by adopting the following formula:
wherein:
t dy is the surface temperature; θ dy The temperature amplitude of the ground surface is the annual amplitude; t is t f Is the additional value of the ground temperature; w (w) y Is the temperature annual amplitude frequency; y is the depth of the ground; a, a y Is the temperature conductivity of the formation material.
Step 2, executing the flow model in the three-dimensional model of the ventilation hole by taking the air supply boundary of the ventilation hole and the temperature boundary of the wall surface of the ventilation hole determined in the step 1 as boundary conditions, and carrying out simulation on fluid in the ventilation hole by the flow model to output simulated air parameters of an outlet of the ventilation hole and a temperature and humidity cloud picture of a section of the ventilation hole; wherein the air parameters of the vent outlet comprise the temperature t of the dry bulb of the vent outlet T2 Relative humidity of air at vent hole outletAir at outlet of ventilation holeMoisture content d T2 Enthalpy of air at vent outlet i T2 ；
In the step, when the flow model simulates the fluid in the ventilation hole, a section is selected every set distance in the three-dimensional model of the ventilation hole, each section has the average temperature of the section, and the three-dimensional model of the ventilation hole is structured to be grid, so that the simulation is performed.
Step 3, detecting the precision of the fluid mechanics model of the ventilation tunnel according to the temperature and humidity cloud picture of the section of the ventilation tunnel, and executing step 4 if the detection passes; if the detection does not pass, returning to the step 2, and correcting the fluid mechanics model of the ventilation tunnel;
and step 4, determining a dehumidification scheme adopted by the vent outlet according to the vent outlet air parameters:
step 4.1, giving the air quantity G of the factory building 1 ；
Step 4.2, determining parameters of the dehumidifier, including: rated air quantity G of single dehumidifier c The dehumidification efficiency parameter gamma of the single dehumidifier, the input power N of the single dehumidifier and the rated dehumidification capacity W of the single dehumidifier c ；
Step 4.3, determining an initial value of the number n of dehumidifier units required to be arranged at the outlet of the ventilating hole;
step 4.4, employing equation Q 1 ＝γ*W c Obtaining the actual refrigerating capacity Q of a single dehumidifier 1 The method comprises the steps of carrying out a first treatment on the surface of the Using formula Q 2 ＝Q 1 +nN, the total heat dissipation Q of n dehumidifier is obtained 2 ；
Step 4.5, obtaining the outlet air moisture content d of the n dehumidifiers by adopting the following formula c ：
Step 4.6, according to the outlet air moisture content d of the n dehumidifiers c Obtaining the corresponding saturated air dry bulb temperature t by searching the enthalpy-humidity diagram c0 ；
The temperature of the dry bulb of the outlet air of the dehumidifier is obtained by adopting the following stepst c The temperature of the air dry bulb at the outlet of the dehumidifier after the heat of the dehumidifier is increased;
step 4.7, according to the temperature t of the dry bulb of the outlet air of the dehumidifier c Moisture content d of outlet air c Searching an enthalpy-humidity diagram to obtain the corresponding enthalpy i of the outlet air of the dehumidifier c ；
Step 4.8, discharging a part of air at the outlet of the ventilating hole after being treated by n dehumidifiers; the other part is not processed by n dehumidifier; the air which is not processed by the dehumidifier and the air which is discharged after being processed by n dehumidifiers form mixed air which is conveyed into a factory building; the moisture content d of the mixed wind is obtained by the following formula H And enthalpy i of mixed wind H ：
G 0 ＝G 1 -nG c
Wherein:
G 1 the air quantity of the factory building; g 0 The air quantity is the air quantity which is not processed by the dehumidifier;
step 4.9, according to the moisture content d of the mixed wind H And enthalpy i of mixed wind H Obtaining the dry bulb temperature t of the mixed air by searching the enthalpy-humidity diagram H And the relative humidity of the mixed wind
Step 4.10, judging the dry bulb temperature t of the mixed air H Whether is greater than the lower limit value t of the dry bulb temperature of the factory building x At the same time, the relative humidity of the mixed windWhether is lower than the upper limit value of the relative humidity of the factory building>If the number of the dehumidifier is satisfied, the number n of the dehumidifier at the moment is the number of the finally determined dehumidifier arranged at the outlet of the ventilating hole, and a dehumidification scheme is obtained; if not, the number n of the dehumidifier is increased by 1, and the process returns to the step 4.4 for cyclic execution.
One specific embodiment is described below:
step 101: acquiring relevant data such as meteorological parameters, soil parameters, geometric parameters, air quantity and the like of a region where a pumped storage power station is located;
in practical application, the acquired related data includes:
(1) Meteorological parameters
Air dry bulb temperature t at inlet of ventilation tunnel T0 ＝28.2℃；
Relative humidity of air at inlet of ventilation tunnel
(2) Soil parameters
Surface temperature t dy ＝10.2℃；
The buried depth Y is 0-380 m;
annual amplitude of ground surface temperature theta dy ＝17.6℃；
Thermal conductivity coefficient a of formation material y ＝0.00166m 2 /h；
Temperature annual wave frequency w y ＝0.00717 1/h；
Added value t of ground temperature f ＝0℃；
Ventilation hole wall moisture dispersion w=2.2 g/m 2 ·h；
(3) Geometric parameters
Full length l=19021m of ventilation hole;
ventilation hole entrance cross-sectional area a=44m 2 ；
Ventilation hole wall areaB＝47950m 2 ；
(4) Other parameters
Ventilation hole air volume g= 418000m 3 /h；
Factory building air volume G 1 ＝170000m 3 /h。
Step 102: determining the temperature boundary of the wall surface of the ventilation hole:
using the formulaAnd obtaining the wall temperature t corresponding to each buried depth Y of the ventilation hole.
According to the wall temperature calculation result, the ground burial depths with the temperature difference less than 1 ℃ are set to be the same wall area, and the area temperature is set to be the wall temperature average value corresponding to the shallowest and the deepest ground burial depths of the area, so that the areas with different ground burial depths of the ventilation holes are divided. In this example, the wall temperature was maintained at 10.2 ℃ at y=0 to 40m, t=24.15 to 10.2 ℃, and at y=40 to 380 m.
Step 103: calculating ventilation hole inlet air corrected relative humidity
Moisture content of air at inlet of ventilation hole Wherein standard atmospheric pressure atm=101325 Pa.
Total moisture dissipation w of ventilation tunnel b =wxb=2.247950×0.001= 105.49kg/h, and this part of the wet load is folded into the fresh air moisture content to obtain the corrected moisture content of the inlet air of the ventilation tunnel According to the air inlet of the ventilation holeTemperature t of air-drying ball T0 And ventilation hole inlet air correction moisture content d T1 Searching the enthalpy-humidity diagram to obtain the corresponding corrected relative humidity of the inlet air of the ventilating hole
Step 104: determining boundaries of the ventilation hole hydrodynamic model therefrom, comprising:
(1) Air supply boundary of ventilation hole
Air dry bulb temperature t at inlet of ventilation tunnel T0 ＝28.2℃；
Relative humidity correction for ventilation tunnel inlet air
Ventilation hole inlet wind speed v=g/a= 418000/3600/44 =2.64 m/s;
(2) Temperature boundary of ventilation hole wall
A ventilation hole wall temperature t list;
the ventilation hole simulates the wall moisture dispersion w' =0.
Step 105: and determining a three-dimensional model of the ventilation hole according to the geometric parameters of the pumped storage power station, including the section area A of the inlet of the ventilation hole, the wall area B of the ventilation hole and the whole length L of the ventilation hole.
Step 106: ICEM and fluent software are applied, a flow model is determined to be an RNG k-epsilon model, a ventilation hole inlet is set to be a ventilation hole-inlet, a ventilation hole outlet is set to be an outflow, a ventilation hole air supply boundary and a ventilation hole wall temperature boundary are set, simulation is carried out, and ventilation hole outlet air parameters and a ventilation hole cross section temperature and humidity cloud picture are output;
specifically, in practical application, after the ventilation hole is 1000m away from the inlet, a ventilation hole section l_i is taken every 100m, the average temperature t_i of the ventilation hole section l_i is equal to the total section number i=1, and the distances from the inlet are respectively: ventilation hole cross-sections l_1=1000, l_2=1100 m, l_3=1200 m … l_10=1900 m. The structured grids are divided, the number of the grids is 192 ten thousand, the grid quality is 0.89, and the simulation conditions are met.
The simulation results include:
temperature t of air dry bulb at outlet of ventilation hole T2 ＝13.8℃；
Relative humidity of air at vent hole outlet
Moisture content d of air at outlet of ventilation hole T2 ＝9.84g/kg；
Enthalpy i of air at outlet of ventilation hole T2 ＝38.75kJ/kg；
And a temperature and humidity cloud picture of each section of the ventilation hole.
Step 107: and detecting the precision of the fluid mechanics model of the ventilation tunnel according to the temperature and humidity cloud image of the section of the ventilation tunnel.
In this example, the comparison between the simulated temperatures of different sections of the ventilation hole and the measured temperatures is shown in table 1 and fig. 2.
Table 1: temperature contrast
As can be seen from the table 1, the average relative error is less than or equal to 15 percent, and the accuracy and precision requirements of the ventilation tunnel fluid mechanics model are met.
Step 108: and determining a dehumidification scheme adopted by the vent outlet according to the vent outlet air parameters:
rated dehumidification W of single dehumidifier is selected c =15 kg/h, rated air volume G c ＝4000m 3 A dehumidifier of a certain model of/h. Its dehumidifier input power n=7.3 kW, dehumidification efficiency parameter gamma=0.68, rated dehumidification Q of single dehumidifier 1 Total heat dissipation Q of n dehumidifier (15 kW) with n dehumidifier units 2 。
When n=15, the total heat dissipation is 216.6kW; calculating the outlet air moisture content of n dehumidifierSaturation at this time is obtained from the psychrometric chartAir dry bulb temperature t c0 =10.01 ℃; after being heated by the heat dissipation capacity of the dehumidifier, the temperature of the air dry bulb at the outlet of the dehumidifier is +.> Obtaining the enthalpy k of the outlet air of the dehumidifier through the enthalpy-humidity diagram c =40.62 kJ/kg; calculating untreated air volume G 0 ＝G 1 -nG c ＝122000m 3 Calculating the moisture content of the mixed wind according to the data>Enthalpy of mixed windThe dry bulb temperature t of the mixed air is calculated through an enthalpy-humidity diagram H Relative humidity of mixed wind =16.31℃>In practical application, the lower limit value t of the temperature of the dry bulb of the factory building x =15 ℃, upper limit value of plant relative humidity +.>Therefore, when 15 dehumidifiers are arranged, the temperature and humidity requirements of the factory are met, and the dehumidification scheme is obtained.
Compared with the prior art, the technical scheme of the invention has the following beneficial effects:
the invention provides an optimization method of a dehumidifying scheme of a pumped storage power station plant based on numerical simulation, which is characterized in that the change of flow field characteristic parameters is obtained by simulating the air flow in a ventilation hole of the pumped storage power station, so that the air parameters of an outlet of the ventilation hole are obtained, and the minimum number of dehumidifier arrangements meeting the temperature and humidity requirements in the plant is obtained by the influence of the number of dehumidifiers on the air parameters in the plant, so that the energy conservation is maximized. The invention has accurate simulation process, high simulation speed and high simulation result precision, and can realize that the optimal number of the dehumidifier arrangements can be obtained in real time according to the inlet parameters of the ventilating holes, thereby starting the dehumidifiers with corresponding numbers and ensuring that the temperature and the humidity in the factory building meet the requirements.
The foregoing is merely a preferred embodiment of the present invention and it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present invention, which is also intended to be covered by the present invention.
Claims (6)
1. The optimization method of the dehumidification scheme of the pumped storage power station plant based on numerical simulation is characterized by comprising the following steps of:
step 1, establishing a fluid mechanics model of a ventilation hole, wherein the fluid mechanics model comprises a three-dimensional model of the ventilation hole, an air supply boundary of the ventilation hole, a wall temperature boundary of the ventilation hole and a flow model;
wherein the ventilation hole air supply boundary comprises the air dry bulb temperature t at the inlet of the ventilation hole T0 Relative humidity correction for ventilation tunnel inlet airThe inlet wind speed v of the ventilation hole;
the ventilation hole wall temperature boundary comprises a ventilation hole wall temperature boundary and a ventilation hole simulation wall moisture dispersion amount; wherein, ventilation hole wall temperature boundary refers to: setting the value of the ground depth Y to obtain the wall temperature t corresponding to each ground depth Y in the ventilation hole, thereby forming a ventilation hole wall temperature boundary;
step 2, executing the flow model in the three-dimensional model of the ventilation hole by taking the air supply boundary of the ventilation hole and the temperature boundary of the wall surface of the ventilation hole determined in the step 1 as boundary conditions, and carrying out simulation on fluid in the ventilation hole by the flow model to output simulated air parameters of an outlet of the ventilation hole and a temperature and humidity cloud picture of a section of the ventilation hole; wherein the ventilation hole outlet air parameters comprise the ventilation hole outlet air temperature t T2 Relative humidity of air at vent hole outletMoisture content d of air at outlet of ventilation hole T2 Enthalpy of air at vent outlet i T2 ；
Step 3, detecting the precision of the fluid mechanics model of the ventilation tunnel according to the temperature and humidity cloud picture of the section of the ventilation tunnel, and executing step 4 if the detection passes; if the detection does not pass, returning to the step 2, and correcting the fluid mechanics model of the ventilation tunnel;
and step 4, determining a dehumidification scheme adopted by the vent outlet according to the vent outlet air parameters:
step 4.1, giving the air quantity G of the factory building 1 ；
Step 4.2, determining parameters of the dehumidifier, including: rated air quantity G of single dehumidifier c The dehumidification efficiency parameter gamma of the single dehumidifier, the input power N of the single dehumidifier and the rated dehumidification capacity W of the single dehumidifier c ；
Step 4.3, determining an initial value of the number n of dehumidifier units required to be arranged at the outlet of the ventilating hole;
step 4.4, employing equation Q 1 ＝γ*W c Obtaining the actual refrigerating capacity Q of a single dehumidifier 1 The method comprises the steps of carrying out a first treatment on the surface of the Using formula Q 2 ＝Q 1 +nN, the total heat dissipation Q of n dehumidifier is obtained 2 ；
Step 4.5, obtaining the outlet air moisture content d of the n dehumidifiers by adopting the following formula c ：
Step 4.6, according to the outlet air moisture content d of the n dehumidifiers c Obtaining the corresponding saturated air dry bulb temperature t by searching the enthalpy-humidity diagram c0 ；
The temperature t of the dry bulb of the outlet air of the dehumidifier is obtained by adopting the following steps c The temperature of the air dry bulb at the outlet of the dehumidifier after the heat of the dehumidifier is increased;
step 4.7, according to the temperature t of the dry bulb of the outlet air of the dehumidifier c Moisture content d of outlet air c Searching an enthalpy-humidity diagram to obtain the corresponding enthalpy i of the outlet air of the dehumidifier c ；
Step 4.8, discharging a part of air at the outlet of the ventilating hole after being treated by n dehumidifiers; the other part is not processed by n dehumidifier; the air which is not processed by the dehumidifier and the air which is discharged after being processed by n dehumidifiers form mixed air which is conveyed into a factory building; the moisture content d of the mixed wind is obtained by the following formula H And enthalpy i of mixed wind H ：
G 0 ＝G 1 -nG c
Wherein:
G 1 the air quantity of the factory building; g 0 The air quantity is the air quantity which is not processed by the dehumidifier;
step 4.9, according to the moisture content d of the mixed wind H And enthalpy i of mixed wind H Obtaining the dry bulb temperature t of the mixed air by searching the enthalpy-humidity diagram H And the relative humidity of the mixed wind
Step 4.10, judging the dry bulb temperature t of the mixed air H Whether is greater than the lower limit value t of the dry bulb temperature of the factory building x At the same time, the relative humidity of the mixed windWhether is lower than the upper limit value of the relative humidity of the factory building>If the number of the dehumidifier is satisfied, the number n of the dehumidifier at the moment is the number of the finally determined dehumidifier arranged at the outlet of the ventilating hole, and a dehumidification scheme is obtained; if not, the number n of the dehumidifier is increased by 1, and the process returns to the step 4.4 for cyclic execution.
2. The optimization method of the dehumidification scheme of the pumped storage power station plant based on numerical simulation according to claim 1, wherein in the step 1, the method for establishing the three-dimensional model of the ventilation hole is as follows: obtaining a ventilation hole structure parameter; establishing a three-dimensional model of the ventilation tunnel according to the ventilation tunnel structure parameters; the ventilation hole structure parameters comprise a ventilation hole inlet section area A, a ventilation hole wall surface area B and a ventilation hole total length L.
3. The optimization method of a pumped storage power plant dehumidification scheme based on numerical simulation according to claim 1, wherein in step 1, the relative humidity of air at the inlet of a ventilation hole is correctedThe determining method of (1) comprises the following steps:
step A1, obtaining the moisture content d of air at the inlet of the ventilation hole by adopting the following formula T0 ：
Wherein:
air relative humidity is input to the ventilation hole; p (P) sb The saturated vapor pressure of the air at the inlet of the ventilation hole; atm is standard atmospheric pressure;
step A2, adopting the following stepsObtaining the total moisture dissipation w of the ventilation tunnel b ：
w b ＝w*B
Wherein:
w is the moisture dispersion of the wall surface of the ventilation hole;
b is the wall area of the ventilation hole;
step A3, obtaining the corrected moisture content d of the inlet air of the ventilating hole by adopting the following steps T1 ：
Wherein: g is the air quantity of the ventilation hole;
step A4, according to the temperature t of the dry ball of the inlet air of the ventilating hole T0 And ventilation hole inlet air correction moisture content d T1 Searching the enthalpy-humidity diagram to obtain the corresponding corrected relative humidity of the inlet air of the ventilating hole
4. The optimization method of a dehumidification scheme of a pumped storage power station plant based on numerical simulation according to claim 1, wherein in step 1, the method for determining the inlet wind speed v of the ventilation tunnel is as follows: using the formulaAnd obtaining the inlet wind speed v of the ventilating hole.
5. The optimization method of the dehumidification scheme of the pumped storage power station plant based on numerical simulation according to claim 1, wherein in the step 1, the wall temperature t corresponding to each buried depth Y of the ventilation tunnel is obtained by adopting the following formula:
wherein:
t dy is the surface temperature; θ dy The temperature amplitude of the ground surface is the annual amplitude; t is t f Is the additional value of the ground temperature; w (w) y Is the temperature annual amplitude frequency; y is the depth of the ground; a, a y Is the temperature conductivity of the formation material.
6. The optimization method of the dehumidification scheme of the pumped storage power station plant based on numerical simulation according to claim 1, wherein in the step 2, when the flow model simulates the fluid in the ventilation hole, a section is selected every set distance in the three-dimensional model of the ventilation hole, each section has the average temperature of the section, and the three-dimensional model of the ventilation hole is structured to be grid, so that simulation is performed.
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