CN110096845B - Design calculation method of mixed-flow closed cooling tower - Google Patents
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Abstract
The invention provides a design calculation method of a mixed flow type closed cooling tower, which is characterized in that according to environmental weather conditions, cooling tasks and specifications of a heat exchange tube, thermal analysis is carried out according to an energy conservation and heat transfer basic formula and a heat transfer and mass transfer empirical formula of the heat exchange tube, a heat exchanger structure is designed, required spray water quantity and fan air quantity are calculated, and the outlet temperature of a medium, the average spray water temperature, the outlet air parameters, the spray water evaporation quantity and the water supplementing quantity are predicted. Besides the heat transfer calculation of the traditional heat exchanger design, the design also adds mass transfer calculation of a wet area part, so that the closed tower design is more comprehensive and accurate. The design method can standardize and optimize the design flow of the mixed flow closed cooling tower, improve the heat exchange efficiency of the cooling tower, reduce the area allowance of the heat exchanger, reduce the material consumption and reduce the cost; and effectively reduce spraying water quantity and fan air quantity, save running cost and avoid resource waste.
Description
Technical Field
The design method is suitable for design calculation of the mixed flow type closed cooling tower, and belongs to the field of cooling tower design. The closed cooling tower is particularly suitable for closed cooling towers with upper coils and lower fillers, wherein the top of a coil area is provided with air inlet, and the side surface of the filler area is provided with air inlet.
Background
The mixed flow type closed cooling tower has good cooling effect, saves the usage amount of the coil pipe, saves the manufacturing cost and has wide market prospect. However, the design method of the domestic mixed flow closed tower is still immature, and many manufacturers can only estimate according to engineering experience, so that the cooling effect is not up to standard or the consumption is high, and the cost is high, thereby causing resource waste.
In the mixed flow closed cooling tower, a heat exchange coil and a filler are core components, the size of the heat exchange coil and the filler are determined and designed to be complex in calculation, the cooling tower cannot be accurately designed due to inaccurate calculation, and the performance of the cooling tower cannot be guaranteed.
The traditional thermal analysis of the cooling tower focuses on heat transfer calculation, but the heat of the medium in the pipe is transferred to the air by the vaporization latent heat of the spray water to take away the heat, so the heat transfer and mass transfer calculation of the spray water outside the pipe and the air is also an indispensable important part in the thermal analysis of the closed cooling tower, and the structural size of the cooling tower is designed more reasonably by comprehensively considering the heat transfer calculation, the mass transfer calculation and the resistance calculation.
Disclosure of Invention
In order to solve the problems, the design calculation method of the closed cooling tower consisting of the heat exchange tubes, the fillers and the like is optimized, the closed cooling tower is subjected to thermal analysis by utilizing an energy conservation and heat transfer basic formula and a heat transfer and mass transfer empirical formula of the heat exchange tubes, a heat exchange tube heat exchanger, the fillers and the water spraying quantity and the air quantity required by calculation are designed, the predicted medium outlet temperature, the spray water average temperature, the tower outlet air parameters, the spray water evaporation quantity and the water supplementing quantity are calculated through checking, and the optimal design of the mixed flow type closed cooling tower is guided.
In order to achieve the above object, the present invention is realized by the following design scheme: a design calculation method of a mixed-flow closed cooling tower comprises the following steps:
s1: determining environmental weather conditions: environmental meteorological conditions: the relative humidity phi is calculated according to a thermodynamic calculation formula by the ambient atmospheric pressure Pa (kPa), the ambient air dry bulb temperature theta (DEG C) and the ambient air wet bulb temperature tau (DEG C) i Moisture content x of the inlet air i The dry bulb temperature corresponds to the saturated steam partial pressure p θ The wet bulb temperature corresponds to the saturated steam partial pressure p τ Density ρ of wet air entering tower i Enthalpy value h of inlet air i 。
S2: determining a cooling task: single tower cooling circulation water quantity Q (m) 3 /h), circulating water inlet tower water temperature T 1 Water temperature T from tower 2 。
S3: setting the distribution proportion of the heat load in the cooling of the coil area and the filling area: first, the total heat load Q is calculated from the cooling task k And determining the respective heat loads of the disc zone and the filler zone according to the filler zone distribution ratio X.
S4: and determining the specification of the coil pipe and initially determining the structure of the heat exchanger. Determining ellipsesThe diameter do and the wall thickness delta of the coil pipe, the length L 'of the single-row pipe, the number P' of layers of each flow pipe, and the equivalent diameter d are calculated is The number of tubes per flow is G', the number of tubes per row is G, the number of tube rows is P, and the tube core distance per row is S 1 Every row of heart spaces S 2 。
S5: calculating the flow rate in the pipe, judging whether the flow rate in the pipe is between 0.5 and 1.5m/S, if so, continuing the next step, and if not, returning to S4 to rearrange the pipe bundle;
s6: setting the air distribution V in the disc area a1 。
S7: calculating the windspeed u of the head-on of the disc zone a '. And judging whether the wind speed is between 0.4 and 4m/S, if so, continuing the next step, if not, returning to S4 to rearrange the tube bundles, if so, continuing the next step, and if not, returning to S6.
S8: setting average spray water temperature T w 。
S9: setting the assumed spray water quantity V w . Assuming a unit heat load water distribution v w The required spray water quantity V is estimated initially w . There are evaporative condenser standards established by the mechanical industry sector in 1982: the maximum water distribution is not more than 0.043m 3 1000kJ, calculating the maximum spraying water quantity V wmax 。
S10: and calculating a heat transfer coefficient q and a heat transfer area F. Respectively calculating heat exchange coefficients a of the outer surface of the pipe and spray water o Convection heat transfer coefficient a of cooling water and wall surface in pipe i Heat conduction resistance R of pipe wall p Dirt thermal resistance R of inner wall of coil pipe i Dirt thermal resistance R of outer wall of coil pipe p Calculating total heat exchange of coil pipes
S11: and calculating the number of the pipe processes n, and taking the actual number of the pipe processes n ', wherein the actual number of the pipe processes n' cannot be smaller than the calculated number of the pipe processes n.
S12: calculating the tower length L, the tower width B and the coil area height H g 。
S13: calculating mass transfer coefficient k m . According to the convection heat exchange coefficient a' between the spray water and the air, a mass transfer coefficient k is obtained m 。
S14: the wet zone cooling area was calculated. And obtaining the cooling area of the wet area according to the water film and the spraying area.
S15: calculating the water film area cooling number M w And the number of heat transfer units NTU. And calculating the water film area cooling number and the heat transfer unit number according to the coil heat exchange coefficient and the mass transfer coefficient.
S16: calculate the spray water temperature T w '. According to the coil structure, air distribution and spray water quantity, spray water temperature T can be calculated w ’。
S17: comparing and checking whether the spray water temperature is equal to the assumed spray water average temperature. If the two are balanced, the next step can be continued; if not, the process returns to S8 to reset the spray level temperature.
S18: calculating the medium outlet temperature T 2 '. And when the temperature is lower than the water outlet temperature T2, carrying out the next step, otherwise returning to S6 to increase the air distribution quantity of the coil area until the temperature of the medium outlet is lower than or equal to the designed water outlet temperature.
S19: setting the size and length L of the filler t Height H t Depth B t 。
S20: setting the air volume V of a filling area a2 。
S21: calculating the water inlet temperature T of spray water in the filling area w1 ' Water outlet temperature T w2 ’。
S22: the cooling characteristic number Ω and the cooling task number N are calculated. And judging whether the cooling characteristic number is larger than the cooling task number, if so, carrying out the next step, otherwise, returning to S20.
S23: calculating disc zone resistance ΔP 1 The method comprises the steps of carrying out a first treatment on the surface of the Including air inlet resistance, air flow turning resistance, water distribution resistance, coil resistance, water collector resistance, and air duct resistance.
S24: calculating the packing region resistance DeltaP 2 The method comprises the steps of carrying out a first treatment on the surface of the Comprises air inlet resistance, shutter resistance, water distribution resistance, filler resistance, water collector resistance and air duct resistance.
S25: judging coil area resistance delta P 1 And packing region resistance ΔP 2 Whether or not they are equal; if so, the process goes to the next step, otherwise, the process returns to S19.
S26: judging coil area resistance delta P 1 And packing region resistance ΔP 2 Whether within a reasonable range; if so, the next step is performed, otherwise, the process returns to S4.
S27: and outputting a design result.
The invention has the beneficial effects that: the design calculation method of the mixed flow type closed cooling tower reduces the material consumption of the heat exchange coil, reasonably distributes the air quantity of a coil filler area, reduces the spraying water quantity, improves the water recycling rate and reduces the industrial water consumption. The design method comprises heat transfer analysis, mass transfer analysis and resistance analysis when the mixed flow closed tower is designed, provides a mature closed tower design theory for the production of the conventional unconventional closed tower, improves heat exchange efficiency, reduces production cost, saves operation cost, and enables the closed tower to be more energy-saving and efficient.
Drawings
Other features, objects and advantages of the present invention will become more apparent upon reading of the detailed description of non-limiting embodiments, given with reference to the accompanying drawings in which:
FIG. 1 is a schematic flow chart of a design calculation method of a mixed-flow closed cooling tower;
Detailed Description
S1: determining environmental weather conditions: environmental meteorological conditions: the relative humidity phi is calculated according to a thermodynamic calculation formula by the ambient atmospheric pressure Pa (kPa), the ambient air dry bulb temperature theta (DEG C) and the ambient air wet bulb temperature tau (DEG C) i Moisture content x of the inlet air i The dry bulb temperature corresponds to the saturated steam partial pressure p θ The wet bulb temperature corresponds to the saturated steam partial pressure p τ Density ρ of wet air entering tower i Enthalpy value h of inlet air i 。
S2: determining a cooling task: single tower cooling circulation water quantity Q (m) 3 /h), circulating water inlet tower water temperature T 1 Water temperature T from tower 2 。
S3: setting the distribution proportion of the heat load in the cooling of the coil area and the filling area: first, the total heat load Q is calculated from the cooling task k And determining the respective heat loads of the disc zone and the filler zone according to the filler zone distribution ratio X.
S4: determining discAnd (5) the specification of the tube and the structure of the heat exchanger are determined. Determining the pipe diameter do and the wall thickness delta of an elliptic coil, the length L 'of a single-row pipe, the number of layers P' of each flow pipe, and calculating the equivalent diameter d is The number of tubes per flow is G', the number of tube passes is N, the number of tubes per row is G, the number of tube rows is P, and the tube core distance per row is S 1 Every row of heart spaces S 2 。
S5: calculating the flow rate in the pipe, judging whether the flow rate in the pipe is between 0.5 and 1.5m/S, if so, continuing the next step, and if not, returning to S4 to rearrange the pipe bundle;
s6: setting the air distribution V in the disc area a1 。
S7: calculating the windspeed u of the head-on of the disc zone a '. And judging whether the wind speed is between 0.4 and 4m/S, if so, continuing the next step, if not, returning to S4 to rearrange the tube bundles, if so, continuing the next step, and if not, returning to S6.
S8: setting average spray water temperature T w 。
S9: setting the assumed spray water quantity V w . Assuming a unit heat load water distribution v w The required spray water quantity V is estimated initially w . There are evaporative condenser standards established by the mechanical industry sector in 1982: the maximum water distribution is not more than 0.043m 3 1000kJ, calculating the maximum spraying water quantity V wmax 。
S10: and calculating a heat transfer coefficient q and a heat transfer area F. Respectively calculating heat exchange coefficients a of the outer surface of the pipe and spray water o Convection heat transfer coefficient a of cooling water and wall surface in pipe i Heat conduction resistance R of pipe wall p Dirt thermal resistance R of inner wall of coil pipe i Dirt thermal resistance R of outer wall of coil pipe p Calculating the total heat exchange coefficient of the coil pipe
S11: and calculating the number of the pipe processes n, and taking the actual number of the pipe processes n ', wherein the actual number of the pipe processes n' cannot be smaller than the calculated number of the pipe processes n.
S12: calculating the tower length L, the tower width B and the coil area height H g 。
S13: calculating mass transfer coefficient k m . According to the convective heat transfer coefficient a' between the shower water and the air,obtaining mass transfer coefficient k m 。
S14: the wet zone cooling area was calculated. And obtaining the cooling area of the wet area according to the water film and the spraying area.
S15: calculating the water film area cooling number M w And the number of heat transfer units NTU. And calculating the water film area cooling number and the heat transfer unit number according to the coil heat exchange coefficient and the mass transfer coefficient.
S16: calculate the spray water temperature T w '. According to the coil structure, air distribution and spray water quantity, spray water temperature T can be calculated w ’。
S17: comparing and checking whether the spray water temperature is equal to the assumed spray water average temperature. If the two are balanced, the next step can be continued; if not, the process returns to S8 to reset the spray level temperature.
S18: calculating the medium outlet temperature T 2 '. And when the temperature is lower than the water outlet temperature T2, carrying out the next step, otherwise returning to S6 to increase the air distribution quantity of the coil area until the temperature of the medium outlet is lower than or equal to the designed water outlet temperature.
S19: setting the size and length L of the filler t Height H t Depth B t 。
S20: setting the air volume V of a filling area a2 。
S21: calculating the water inlet temperature T of spray water in the filling area w1 ' Water outlet temperature T w2 ’。
S22: the cooling characteristic number Ω and the cooling task number N are calculated. And judging whether the cooling characteristic number is larger than the cooling task number, if so, carrying out the next step, otherwise, returning to S20.
S23: calculating disc zone resistance ΔP 1 The method comprises the steps of carrying out a first treatment on the surface of the Including air inlet resistance, air flow turning resistance, water distribution resistance, coil resistance, water collector resistance, and air duct resistance.
S24: calculating the packing region resistance DeltaP 2 The method comprises the steps of carrying out a first treatment on the surface of the Comprises air inlet resistance, shutter resistance, water distribution resistance, filler resistance, water collector resistance and air duct resistance.
S25: judging coil area resistance delta P 1 And packing region resistance ΔP 2 Whether or not they are equal; if so, the process goes to the next step, otherwise, the process returns to S19.
S26: judging coil area resistance delta P 1 And packing region resistance ΔP 2 Whether within a reasonable range; if so, the next step is performed, otherwise, the process returns to S4.
S27: and outputting a design result.
Example 1. Environmental meteorological conditions: dry bulb temperature θ31.5deg.C, wet bulb temperature τ28deg.C, atmospheric pressure: 99.4kPa.
Determining a cooling task: single tower cooling water quantity Q100m 3 /h, inlet water temperature T 1 40 ℃ outlet water temperature T 2 Is 35 ℃.
The total heat dissipation load 577KW was calculated, the heat load was distributed, the packing area was 50%, about 288.5KW, the coil area was 50%, about 288.5KW.
Setting the structural size of a coil pipe, selecting stainless steel materials, and the specification of a heat exchange tube: the pipe diameter is 16mm, the wall thickness is 0.8mm, the core distance of each pipe is 0.032m, the longitudinal core distance of each pipe is 0.07m, the coil pipe length is 3.2m, each layer of 4 layers of pipe is 39/40 pipes. The flow rate in the tube was 1.07m/s, within a reasonable range.
Setting the air quantity 37000m of the air distribution quantity in the disc area 3 And/h, the wind speed at the head-on is 2.5m/s and is between 1.4 and 4 m/s. Setting average spray water temperature 34.38 ℃ and spray water quantity 18.9m 3 /h, at a minimum spray water volume of 26m 3 /h and maximum spray water quantity 89m 3 Between/h.
Calculated heat exchange coefficientIs 1276W/(m) 2 Temperature of the heat transfer area 94m 2 Calculating the coil Guan Chengshu n3.7, taking 4 passes, and the actual heat transfer area is 101.7m 2 . Calculating the tower length L3.4m, the tower width B2.56m and the coil height H g 1.12m。
Calculating the mass transfer coefficient of spray water to air of 0.23 kg/(m) 2 s.DELTA.d), the cooling area of the wet zone was estimated to be 131m based on the coil structure and the amount of water sprayed 2 The water film area cooling number Mw was calculated to be 4.64 and the heat transfer unit number NTU was calculated to be 2.25.
Then the average spray water temperature is 34.38 ℃ which is the same as the initial spray water temperature, the calculated tower water temperature is 34.97 ℃ which is lower than the designed tower water temperature by 35 ℃.
Setting the dimension length of the filler to be 3.2m, the height to be 1.8m and the depth to be 1.3m, calculating the cooling task number N to be 0.55 according to a filler characteristic equation, and the cooling characteristic number omega to be 0.6, thereby meeting the design requirement. Adjusting the air quantity of the filling area 52000m 3 And/h, so that the coil area resistance and the packing resistance are 109Pa, the calculated fan motor power is 3.59KW, the fan motor power is 4KW, and the total air quantity is 89000m 3 And/h. And (5) after the calculation is finished, outputting a design result.
While the fundamental and principal features of the invention and advantages of the invention have been shown and described, 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 may be embodied in 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 disclosure describes embodiments, not every embodiment is provided with a separate embodiment, and that this description is provided for clarity only, and that the disclosure is not limited to the embodiments described in detail below, and that the embodiments described in the examples may be combined as appropriate to form other embodiments that will be apparent to those skilled in the art.
Claims (4)
1. The design calculation method of the mixed-flow closed cooling tower is characterized by comprising the following steps of:
s1: determining environmental weather conditions: environmental meteorological conditions: the relative humidity phi is calculated according to a thermodynamic calculation formula by the ambient atmospheric pressure Pa (kPa), the ambient air dry bulb temperature theta (DEG C) and the ambient air wet bulb temperature tau (DEG C) i Moisture in the air entering the towerQuantity x i The dry bulb temperature corresponds to the saturated steam partial pressure p θ The wet bulb temperature corresponds to the saturated steam partial pressure p τ Density ρ of wet air entering tower i Enthalpy value h of inlet air i ；
S2: determining a cooling task: single tower cooling circulation water quantity Q (m) 3 /h), circulating water inlet tower water temperature T 1 Water temperature T from tower 2 ；
S3: setting the distribution proportion of the heat load in the cooling of the coil area and the filling area: first, the total heat load Q is calculated from the cooling task k Determining respective heat loads of the disc zone and the filler zone according to the filler zone distribution ratio X;
s4: determining the specification of a coil pipe and initially determining the structure of a heat exchanger; determining the pipe diameter do and the wall thickness delta of an elliptic coil, the length L 'of a single-row pipe, the number of layers P' of each flow pipe, and calculating the equivalent diameter d is The number of tubes per flow is G', the number of tubes per row is G, the number of tube rows is P, and the tube core distance per row is S 1 Every row of heart spaces S 2 ；
S5: calculating the flow rate in the pipe, judging whether the flow rate in the pipe is between 0.5 and 1.5m/S, if so, continuing the next step, and if not, returning to S4 to rearrange the pipe bundle;
s6: setting the air distribution V in the disc area a1 ；
S7: calculating the windspeed u of the head-on of the disc zone a 'A'; judging whether the wind speed is between 0.4 and 4m/S, if so, continuing to the next step, if not, returning to the step S4 to rearrange the tube bundles, if so, continuing to the next step, and if not, returning to the step S6;
s8: setting average spray water temperature T w ；
S9: setting the assumed spray water quantity V w The method comprises the steps of carrying out a first treatment on the surface of the Assuming a unit heat load water distribution v w The required spray water quantity V is estimated initially w The method comprises the steps of carrying out a first treatment on the surface of the There are evaporative condenser standards established by the mechanical industry sector in 1982: the maximum water distribution is not more than 0.043m 3 1000kJ, calculating the maximum spraying water quantity V wmax ；
S10: calculating a heat transfer coefficient q and a heat transfer area F; respectively calculating heat exchange coefficients a of the outer surface of the pipe and spray water o Convection heat transfer coefficient a of cooling water and wall surface in pipe i Pipe wall guideThermal resistance R p Dirt thermal resistance R of inner wall of coil pipe i Dirt thermal resistance R of outer wall of coil pipe p Calculating the total heat exchange coefficient of the coil pipe；
S11: calculating the number n of the pipe processes, and taking the actual number n 'of the pipe processes, wherein the actual number n' of the pipe processes cannot be smaller than the calculated number n of the pipe processes;
s12: calculating the tower length L, the tower width B and the coil area height H g ；
S13: calculating mass transfer coefficient k m The method comprises the steps of carrying out a first treatment on the surface of the According to the convection heat exchange coefficient a' between the spray water and the air, a mass transfer coefficient k is obtained m ；
S14: calculating the cooling area of the wet area; obtaining a wet area cooling area according to the water film and the spraying area;
s15: calculating the water film area cooling number M w And the number of heat transfer units NTU; calculating the water film area cooling number and the heat transfer unit number according to the coil heat exchange coefficient and the mass transfer coefficient;
s16: calculate the spray water temperature T w 'A'; according to the coil structure, air distribution and spray water quantity, spray water temperature T can be calculated w ’；
S17: comparing and checking whether the spray water temperature is equal to the assumed spray water temperature; if the two are balanced, the next step can be continued; if not, returning to S8 to reset the spray average temperature;
s18: calculating the medium outlet temperature T 2 'A'; when the temperature is lower than the water outlet temperature T2, carrying out the next step, otherwise returning to S6 to increase the air distribution quantity in the disc pipe area until the temperature of the medium outlet is lower than or equal to the designed water outlet temperature;
s19: setting the size and length L of the filling area t Height H t Depth B t ；
S20: setting the air volume V of a filling area a2 ；
S21: calculating the water inlet temperature T of spray water in the filling area w1 ' Water outlet temperature T w2 ’；
S22: calculating a cooling characteristic number omega and a cooling task number N; judging whether the cooling characteristic number is larger than the cooling task number, if so, carrying out the next step, otherwise, returning to S20;
s23: calculating the resistance of the disc region P 1 The method comprises the steps of carrying out a first treatment on the surface of the The wind turbine comprises wind inlet resistance, airflow turning resistance, water distribution resistance, coil resistance, water collector resistance and wind drum resistance;
s24: calculating the resistance P of the packing area 2 The method comprises the steps of carrying out a first treatment on the surface of the Comprises air inlet resistance, shutter resistance, water distribution resistance, filler resistance, water collector resistance and air duct resistance;
s25: judging the resistance P of the coil pipe area 1 And packing region resistance P 2 Whether or not they are equal; if yes, carrying out the next step, otherwise returning to S19;
s26: judging the resistance P of the coil pipe area 1 And packing region resistance P 2 Whether within a reasonable range; if yes, carrying out the next step, otherwise returning to S4;
s27: and outputting a design result.
2. The method for designing and calculating a mixed-flow closed cooling tower according to claim 1, wherein: in the steps S3-S26, the distribution of the heat load of the filling area and the coil area is firstly carried out.
3. The method for designing and calculating a mixed-flow closed cooling tower according to claim 1, wherein: the steps S3-S26 comprise mass transfer coefficient calculation, coil pipe area size design, filler area size design, heat transfer unit number calculation, spray water checking temperature calculation and closed tower medium outlet temperature calculation.
4. The method for designing and calculating a mixed-flow closed cooling tower according to claim 1, wherein: in the steps S3-S26, the design of the coil area size and the design of the packing area size comprehensively consider the balance method of heat and resistance.
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| CN103198199A (en) * | 2012-01-08 | 2013-07-10 | 湖南省电力勘测设计院 | Three dimensional heating calculation method of wet-type counter-flow type natural draft cooling tower |
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