CN111090912A - Co2Design method of closed cooling tower for gas cooling - Google Patents
Co2Design method of closed cooling tower for gas cooling Download PDFInfo
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- 238000001816 cooling Methods 0.000 title claims abstract description 54
- 238000000034 method Methods 0.000 title claims abstract description 25
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 103
- 238000005507 spraying Methods 0.000 claims abstract description 35
- 238000009826 distribution Methods 0.000 claims abstract description 29
- 239000007789 gas Substances 0.000 claims abstract description 22
- 239000000112 cooling gas Substances 0.000 claims abstract description 16
- 238000004519 manufacturing process Methods 0.000 claims abstract description 15
- 230000007613 environmental effect Effects 0.000 claims abstract description 8
- 239000003570 air Substances 0.000 claims description 62
- 239000007921 spray Substances 0.000 claims description 37
- 229920006395 saturated elastomer Polymers 0.000 claims description 11
- 238000004364 calculation method Methods 0.000 claims description 9
- 239000012080 ambient air Substances 0.000 claims description 6
- 239000002826 coolant Substances 0.000 claims description 6
- 238000001704 evaporation Methods 0.000 claims description 4
- 230000008020 evaporation Effects 0.000 claims description 4
- 238000009434 installation Methods 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 4
- 239000013589 supplement Substances 0.000 claims description 4
- 238000004140 cleaning Methods 0.000 claims description 3
- 230000000052 comparative effect Effects 0.000 claims description 3
- 238000002076 thermal analysis method Methods 0.000 abstract description 4
- 238000004134 energy conservation Methods 0.000 abstract description 3
- 238000012938 design process Methods 0.000 abstract 1
- 238000010606 normalization Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 2
- 229910001335 Galvanized steel Inorganic materials 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000003889 chemical engineering Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000008397 galvanized steel Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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Abstract
The invention provides a Co2A design method of a closed cooling tower for gas cooling is characterized in that the specification of a heat exchange tube is selected according to environmental meteorological conditions and Co2 gas cooling requirements, the heat exchanger structure is set according to production practice experience and comprises a transverse tube center distance and a longitudinal tube center distance, a double-layer tube structure is selected for each flow, the heat exchange tube is designed in an inclined mode, thermal analysis is carried out according to an energy conservation, basic formula of heat transfer science and a circular tube heat and mass transfer experience formula, a wet area mass transfer process is considered, a coil heat transfer coefficient and a mass transfer coefficient are calculated, the heat exchanger structure is determined, the air distribution quantity and the spraying water quantity required by the closed cooling tower are obtained, and parameters such as Co2 cooling gas outlet temperature, spraying water average temperature, tower outlet air temperature, moisture content, spraying water. The invention adopts the idea of iterative computation, thus improving the accuracy and the normalization of the design process; the design method is widely applied to enterprise production practice by combining the production experience of the heat exchanger, the design efficiency is improved, and the production cost is reduced.
Description
Technical Field
The design method is suitable for the design calculation of the closed cooling tower for the special cooling medium, and belongs to the field of cooling tower design.
Background
The closed cooling tower has the advantages of water conservation, energy conservation, simple and compact structure, simple installation and maintenance and the like as a novel heat exchange device, has better cooling efficiency compared with the traditional heat exchange device, ensures the cleanness of the cooling medium because the cooling medium is not in direct contact with the outside, and has wide market prospect in the fields of air-conditioning refrigeration and chemical engineering. But domestic Co2The design method of the closed tower for gas cooling is not developed yet at present, most manufacturers estimate the design according to engineering experience or design by referring to the traditional design method, and the heat exchange area margin is large, the energy consumption is highMore materials, high cost, resource waste and the like.
In addition, the traditional closed tower thermal analysis focuses on heat transfer calculation, but the heat of fluid in a pipe is taken away by transferring the latent heat of vaporization of spray water to air, so the heat transfer and mass transfer calculation of spray water and air outside the pipe is also an indispensable important part in the closed cooling tower thermal analysis.
Disclosure of Invention
To solve the above problems, the present invention is directed to Co2The design method of the closed cooling tower for gas cooling is optimized, and the fluid in the pipe is Co by utilizing energy conservation, a basic formula of heat transfer science and an empirical formula of heat transfer and mass transfer2Carrying out thermal analysis on a closed cooling tower of gas, designing a coil heat exchanger, calculating the required spraying water quantity and the fan air quantity, and predicting Co through calculation2The gas outlet temperature, the average temperature of spray water, the tower outlet air parameters, the evaporation capacity of spray water, the water supplement amount and the like, and guides the optimization design of the closed cooling tower.
In order to achieve the above object, the present invention is realized by the following design: co2The design method of the closed cooling tower for gas cooling comprises the following steps:
s1: starting;
s2: determining a single tower cooling task: single tower Co2Gas cooling flow rate Q (m)3H), the state parameters of the inlet and outlet tower are as follows: pressure P of cooling gas1Temperature T of entering tower1Temperature T at tower exit2；
S3: environmental weather conditions: environmental weather conditions: the ambient atmospheric pressure Pa, the ambient air dry bulb temperature theta and the ambient air wet bulb temperature tau are calculated according to a thermodynamic calculation formulaiMoisture content x of air entering the toweriDry bulb temperature corresponds to the partial pressure p of saturated steamθWet bulb temperature corresponds to the partial pressure p of saturated steamτDensity of wet air entering tower rhoiAir entering the tower has enthalpy value hi；
S4: assuming the average temperature t of the spray waterwCalculating the logarithmic mean temperature difference △ Tm；
S5: assumed heat transfer coefficientCalculating the initial estimated heat exchange area F according to △ Tmo；
S6: and selecting the specification of the coil pipe according to production experience, and initially determining the structure of the heat exchanger. Determining the material and outer diameter D of the coiloWall thickness delta, single-row pipe length L, arrangement mode, number of layers P in each process, number of pipes G' in each process, number of pipe passes N, number of pipes G in each row and number of pipe rows P, selecting compact or standard arrangement coil pipes according to production experience, and selecting proper transverse pipe center distance S in consideration of future installation and cleaning work1Distance S from longitudinal pipe center2；
S7: and calculating and designing the heat exchange area. Calculating the heat exchange area F of the coil according to the heat exchanger structure preset in S6, and calculating the weight M of the coil;
s8: the air distribution volume is assumed. Selecting proper unit heat load air distribution volume vaCalculating the air distribution volume V according to the heat loadaThe standard air distribution quantity of the evaporative condenser established by the department of mechanical industry in 1982 is less than 45.3m3Per1000 kJ limited maximum value V of fan air volumeamax；
S9: assuming the amount of water sprayed. Selecting proper unit heat load water distribution volume vwInitial estimation of the required spray water volume Vw. Evaporative condenser standards, established by the mechanical industry division in 1982: the maximum water distribution amount is not more than 0.043m3Per1000 kJ, calculating the maximum spraying water volume Vwmax；
S10: and checking the heat exchange coefficient of the coil. According to the assumptions, the heat exchange coefficients a of the outer surface of the tube and the spray water are respectively calculatedoCoefficient of convective heat transfer a between cooling medium in tube and wall surfaceiThermal conduction resistance R of pipe wallpThermal resistance to fouling of inner wall of coil pipe RiThermal resistance to fouling of coil outer wall RpCalculating the total heat exchange coefficient of the coil
；
S11: comparing and checking heat exchange coefficients K of coils'oAnd assumed heat transfer coefficient Ko. If the heat exchange coefficient of the checking coil is larger than the assumed heat exchange coefficient, continuing to calculate, otherwise, returning to S5 to re-assume the heat exchange coefficient Ko；
S12: and calculating the mass transfer coefficient. Obtaining a mass transfer coefficient k according to the convective heat transfer coefficient a' between the spray water and the airm；
S13: the wet zone cooling area was calculated. Obtaining the cooling area of the wet area according to the water film and the spraying area;
s14: the water film area cooling number Mw and the number of heat transfer units NTU are calculated. Calculating the water film area cooling number and the heat transfer unit number according to the heat exchange coefficient and the mass transfer coefficient of the coil;
s15: tower air parameters are calculated. According to the law of conservation of energy, supposing that the air out of the tower is saturated humid air, calculating the temperature of the air out of the tower, the moisture content of the air out of the tower, and calculating the evaporation capacity and the water supplement capacity of spray water;
s16: and checking the spraying water temperature. Calculating the spraying water temperature tw' according to the structure of the coil, the air distribution quantity and the spraying water quantity;
s17: and comparing and checking whether the spraying water temperature is equal to the assumed average spraying water temperature. If the two are balanced, the tower water temperature can be calculated; if not, returning to S4 to re-assume the average temperature of the spray water;
s18: calculating Co2The gas outlet temperature is cooled. When the check in S17 shows that the spray water temperature is balanced with the assumed average spray water temperature, Co can be obtained2Cooling gas outlet temperature T'2；
S19: comparative Co2The cooling gas outlet temperature and the design outlet temperature. If Co2Cooling gas outlet temperature T'2Above design outlet temperature T2Returning to S8 to increase the initial air distribution quantity and S9 to increase the spraying water quantity until Co2The outlet temperature of the cooling gas is less than or equal to the design outlet temperature;
s20: outputting a design result;
s21: and (6) ending.
The invention has the beneficial effects that: co of the invention2The design method of the closed cooling tower for gas cooling is combined with actual production experience to design a coil structure, and a heat exchange tube inclined double-layer staggered arrangement mode is adopted, so that the structure of the heat exchanger is more compact. And the design method not only comprises the thermodynamic calculation of the heat exchangerAnd mass transfer process of spray water in a wet area is also considered, mass transfer analysis of the closed tower is increased, and design rigor and reliability of the closed tower are increased. And adopting iterative computation idea, repeatedly iterating by assuming medium temperature in the pipe and spray water average temperature, finally determining related parameters of the closed cooling tower, and predicting Co2The temperature of the gas outlet, the spray water and the air out of the tower are equivalent. The design method is widely applied to enterprise production practice by combining the production experience of the heat exchanger, the design efficiency is improved, and the production cost is reduced.
Drawings
Other features, objects and advantages of the invention will become more apparent upon reading of the detailed description of non-limiting embodiments with reference to the following drawings:
FIG. 1 shows a Co of the present invention2The flow diagram of the design method of the closed cooling tower for gas cooling.
Detailed Description
S1: starting;
s2: determining a single tower cooling task: single tower Co2Gas cooling flow rate Q (m)3H), the state parameters of the inlet and outlet tower are as follows: pressure P of cooling gas1Temperature T of entering tower1Temperature T at tower exit2；
S3: environmental weather conditions: environmental weather conditions: the ambient atmospheric pressure Pa, the ambient air dry bulb temperature theta and the ambient air wet bulb temperature tau are calculated according to a thermodynamic calculation formulaiMoisture content x of air entering the toweriDry bulb temperature corresponds to the partial pressure p of saturated steamθWet bulb temperature corresponds to the partial pressure p of saturated steamτDensity of wet air entering tower rhoiAir entering the tower has enthalpy value hi；
S4: assuming the average temperature t of the spray waterwCalculating the logarithmic mean temperature difference △ Tm；
S5, assuming the heat exchange coefficient, calculating the initial estimated heat exchange area F according to △ Tmo；
S6: and selecting the specification of the coil pipe according to production experience, and initially determining the structure of the heat exchanger. Determining the material and outer diameter D of the coiloWall thickness delta, single row of tubesThe length L, the arrangement mode, the number of layers P in each process, the number of pipes G' in each process, the number of pipe passes N, the number of pipes G in each row and the number of pipe rows P are selected, compact or standard arrangement coil pipes are selected according to production experience, and the proper transverse pipe center distance S is selected in consideration of the future installation and cleaning work1Distance S from longitudinal pipe center2；
S7: and calculating and designing the heat exchange area. Calculating the heat exchange area F of the coil according to the heat exchanger structure preset in S6, and calculating the weight M of the coil;
s8: the air distribution volume is assumed. Selecting proper unit heat load air distribution volume vaCalculating the air distribution volume V according to the heat loadaThe standard air distribution quantity of the evaporative condenser established by the department of mechanical industry in 1982 is less than 45.3m3Per1000 kJ limited maximum value V of fan air volumeamax；
S9: assuming the amount of water sprayed. Selecting proper unit heat load water distribution volume vwInitial estimation of the required spray water volume Vw. Evaporative condenser standards, established by the mechanical industry division in 1982: the maximum water distribution amount is not more than 0.043m3Per1000 kJ, calculating the maximum spraying water volume Vwmax；
S10: and checking the heat exchange coefficient of the coil. According to the assumptions, the heat exchange coefficients a of the outer surface of the tube and the spray water are respectively calculatedoCoefficient of convective heat transfer a between cooling medium in tube and wall surfaceiThermal conduction resistance R of pipe wallpThermal resistance to fouling of inner wall of coil pipe RiThermal resistance to fouling of coil outer wall RpCalculating the total heat exchange coefficient of the coil
；
S11: comparing and checking heat exchange coefficients K of coils'oAnd assumed heat transfer coefficient Ko. If the heat exchange coefficient of the checking coil is larger than the assumed heat exchange coefficient, continuing to calculate, otherwise, returning to S5 to re-assume the heat exchange coefficient Ko；
S12: and calculating the mass transfer coefficient. Obtaining a mass transfer coefficient k according to the convective heat transfer coefficient a' between the spray water and the airm；
S13: the wet zone cooling area was calculated. Obtaining the cooling area of the wet area according to the water film and the spraying area;
s14: the water film area cooling number Mw and the number of heat transfer units NTU are calculated. Calculating the water film area cooling number and the heat transfer unit number according to the heat exchange coefficient and the mass transfer coefficient of the coil;
s15: tower air parameters are calculated. According to the law of conservation of energy, supposing that the air out of the tower is saturated humid air, calculating the temperature of the air out of the tower, the moisture content of the air out of the tower, and calculating the evaporation capacity and the water supplement capacity of spray water;
s16: and checking the spraying water temperature. Calculating the spraying water temperature tw' according to the structure of the coil, the air distribution quantity and the spraying water quantity;
s17: and comparing and checking whether the spraying water temperature is equal to the assumed average spraying water temperature. If the two are balanced, the tower water temperature can be calculated; if not, returning to S4 to re-assume the average temperature of the spray water;
s18: calculating Co2The gas outlet temperature is cooled. When the check in S17 shows that the spray water temperature is balanced with the assumed average spray water temperature, Co can be obtained2Cooling gas outlet temperature T'2；
S19: comparative Co2The cooling gas outlet temperature and the design outlet temperature. If Co2Cooling gas outlet temperature T'2Above design outlet temperature T2Returning to S8 to increase the initial air distribution quantity and S9 to increase the spraying water quantity until Co2The outlet temperature of the cooling gas is less than or equal to the design outlet temperature;
s20: outputting a design result;
s21: and (6) ending.
Example 1.
Determining a single tower cooling task: single tower Co2Gas cooling flow rate 1500m3The state parameters of the inlet and outlet tower are as follows: the cooling gas pressure is 3MPa, the tower inlet temperature is 52 ℃, and the tower outlet temperature is 40 ℃;
environmental weather conditions: dry bulb temperature 31.5 ℃, wet bulb temperature 28 ℃, atmospheric pressure: 99.4 kPa. Calculating the relative humidity of 76.786% and the moisture content of air entering the tower to be 0.023kg/kg (DA), wherein the dry bulb temperature corresponds to the saturated steam partial pressure of 4.621kPa, and the wet bulb temperature corresponds to the saturated steam partial pressure of 3.779kPaThe density of wet air entering the tower is 1.124kg/m3The enthalpy of air entering the tower is 90.556 kJ/kg; the heat load was calculated from the cooling duty to be 216.005 kW;
the heat exchange coefficient is assumed to be 69W/(m)2∙ deg.C), the initial average temperature of the spray water is 28 deg.C, and the calculated average logarithmic mean temperature difference is 12 deg.C. Calculating the initial estimated heat exchange area to be 260m2；
The coil pipe structure is set initially: the galvanized steel pipe specification is 25mm multiplied by 1.5mm, the center distance of each row of pipes is 0.045m, the center distance of the longitudinal pipe is 0.039m, the length of the coil pipe is 4.5m, 1 layer of pipe is arranged in each process, 40 pipes are arranged in each process, the total area of the heat exchange pipe is 282.75m2Larger than the initial heat exchange area;
the unit heat load air distribution quantity is initially set to be 70m3/(h ∙ kW), blower wind volume 15120m3The water distribution amount per unit heat load is 2.895kg/(h ∙ kW), and the spraying water amount is 84.863m3/h；
And calculating the total heat exchange coefficient according to the assumed value. Calculating the convection heat transfer coefficient a in the tubeiIs 79.169W/(m)2∙ deg.C, convection heat transfer coefficient a of water film outside pipeoIs 1620.176W/(m)2∙ deg.C, thermal conductivity and resistance 0.00007199 (m)2∙ ℃)/W, neglecting the heat conduction and resistance of the tube wall, calculating the heat exchange coefficient
W/(m2∙ deg.C), the calculated heat transfer coefficient is greater than the assumed heat transfer coefficient. And calculating the mass transfer coefficient of the spray water and the air. The mass transfer coefficients of the shower water and the air outside the elliptical tube are related to the air flow velocity between the tubes, and the mass transfer coefficient is calculated according to an empirical formula to be 0.0626 kg/(m.s. delta d);
estimating the cooling area 215.162m of the wet area according to the parameters such as the structure of the coil pipe, the amount of sprayed water and the like2For calculating the water film area cooling number Mw of 3.57 and the number of heat transfer units NTU of 0.939;
then, the average temperature of the spray water is calculated to be 41.364 ℃ from the above values, which is different from the initial spray water temperature. Adjusting the initial spraying water temperature to make the calculated average spraying water temperature equal to the initial spraying water temperature, wherein the calculated spraying water temperature is 34.812 ℃, and calculating Co2The exit temperature is 41.6 ℃ higher than the designed tower water temperature by 40 ℃. The air distribution quantity, the spraying water quantity, the heat exchange coefficient, the coil structure and the spraying water temperature are increased, so that the judgment conditions can be met. The final air distribution rate is 21600m3The spraying water quantity is 52.636m3H, the coil structure is unchanged, the average temperature of spray water is 33.681 ℃, and Co2And the temperature of the outlet tower is 40.125 ℃, the deviation of the temperature of the outlet tower and the temperature of the outlet tower water required by the design is 0.125 ℃, and the calculation is finished and the design result is output within the error range of the design.
While there have been shown and described what are at present considered the fundamental principles and essential features of the invention and its advantages, it will be apparent to those skilled in the art that the invention is not limited to the details of the foregoing exemplary embodiments, but is capable of other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may include only a single embodiment, and such description is for clarity only, and those skilled in the art will be able to make the description as a whole, and the embodiments may be appropriately combined to form other embodiments as will be apparent to those skilled in the art.
Claims (2)
1. Co2The design method of the closed cooling tower for gas cooling is characterized by comprising the following steps of:
s1: starting;
s2: determining a single tower cooling task: single tower Co2Gas cooling flow rate Q (m)3H), the state parameters of the inlet and outlet tower are as follows: pressure P of cooling gas1Temperature T of entering tower1Temperature T at tower exit2；
S3: environmental weather conditions: environmental weather conditions: the ambient atmospheric pressure Pa, the ambient air dry bulb temperature theta and the ambient air wet bulb temperature tau are calculated according to a thermodynamic calculation formulaiMoisture content x of air entering the toweriDry bulb temperature corresponds to the partial pressure p of saturated steamθWet bulb temperature corresponds to the partial pressure p of saturated steamτDensity of wet air entering tower rhoiAir entering the tower has enthalpy value hi；
S4: assuming the average temperature t of the spray waterwCalculating the logarithmic mean temperature difference △ Tm；
S5, assuming the heat exchange coefficient, calculating the initial estimated heat exchange area F according to △ Tmo；
S6: selecting the specification of the coil pipe according to production experience, and initially determining the structure of the heat exchanger;
determining the material and outer diameter D of the coiloWall thickness delta, single-row pipe length L, arrangement mode, number of layers P in each process, number of pipes G' in each process, number of pipe passes N, number of pipes G in each row and number of pipe rows P, selecting compact or standard arrangement coil pipes according to production experience, and selecting proper transverse pipe center distance S in consideration of future installation and cleaning work1Distance S from longitudinal pipe center2；
S7: calculating the designed heat exchange area;
calculating the heat exchange area F of the coil according to the heat exchanger structure preset in S6, and calculating the weight M of the coil;
s8: assuming air distribution quantity;
selecting proper unit heat load air distribution volume vaCalculating the air distribution volume V according to the heat loadaThe standard air distribution quantity of the evaporative condenser established by the department of mechanical industry in 1982 is less than 45.3m3Per1000 kJ limited maximum value V of fan air volumeamax；
S9: assuming the amount of sprayed water;
selecting proper unit heat load water distribution volume vwInitial estimation of the required spray water volume Vw；
Evaporative condenser standards, established by the mechanical industry division in 1982: the maximum water distribution amount is not more than 0.043m3Per 1000kJ, calculate maximum sprayAmount of water Vwmax；
S10: checking the heat exchange coefficient of the coil;
according to the assumptions, the heat exchange coefficients a of the outer surface of the tube and the spray water are respectively calculatedoCoefficient of convective heat transfer a between cooling medium in tube and wall surfaceiThermal conduction resistance R of pipe wallpThermal resistance to fouling of inner wall of coil pipe RiThermal resistance to fouling of coil outer wall RpCalculating the total heat exchange coefficient of the coil
；
S11: comparing and checking heat exchange coefficients K of coils'oAnd assumed heat transfer coefficient Ko；
If the heat exchange coefficient of the checking coil is larger than the assumed heat exchange coefficient, continuing to calculate, otherwise, returning to S5 to re-assume the heat exchange coefficient Ko；
S12: calculating a mass transfer coefficient;
obtaining a mass transfer coefficient k according to the convective heat transfer coefficient a' between the spray water and the airm；
S13: calculating the cooling area of the wet area;
obtaining the cooling area of the wet area according to the water film and the spraying area;
s14: calculating the water film area cooling number Mw and the heat transfer unit number NTU;
calculating the water film area cooling number and the heat transfer unit number according to the heat exchange coefficient and the mass transfer coefficient of the coil;
s15: calculating tower air parameters;
according to the law of conservation of energy, supposing that the air out of the tower is saturated humid air, calculating the temperature of the air out of the tower, the moisture content of the air out of the tower, and calculating the evaporation capacity and the water supplement capacity of spray water;
s16: checking the spraying water temperature;
calculating the spraying water temperature tw' according to the structure of the coil, the air distribution quantity and the spraying water quantity;
s17: comparing and checking whether the spraying water temperature is equal to the assumed average spraying water temperature;
if the two are balanced, the tower water temperature can be calculated; if not, returning to S4 to re-assume the average temperature of the spray water;
s18: calculating Co2Cooling the gas outlet temperature;
when the check in S17 shows that the spray water temperature is balanced with the assumed average spray water temperature, Co can be obtained2Cooling gas outlet temperature T'2；
S19: comparative Co2Cooling the gas outlet temperature and the design outlet temperature;
if Co2Cooling gas outlet temperature T'2Above design outlet temperature T2Returning to S8 to increase the initial air distribution quantity and S9 to increase the spraying water quantity until Co2The outlet temperature of the cooling gas is less than or equal to the design outlet temperature;
s20: outputting a design result;
s21: and (6) ending.
2. Co according to claim 12The design method of the closed cooling tower for gas cooling is characterized in that: in the steps S4-S19, the coil structure is set according to actual production experience, the wet area is calculated by considering the mass transfer of the wet area, the mass transfer coefficient is considered to determine the average temperature of the spray water, and the Co is predicted2The gas outlet temperature is cooled.
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Address after: Room 1607, building 4, union Fortune Plaza, qiaomeng yuan, no.2177 Tianchen Road, high tech Zone, Jinan City, Shandong Province Applicant after: JINAN LANCHEN ENERGY TECHNOLOGY Co.,Ltd. Address before: 503, block a, No.777, Shunfeng Road, high tech Zone, Jinan City, Shandong Province Applicant before: JINAN LANCHEN ENERGY TECHNOLOGY Co.,Ltd. |
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