CN112100815B - Surface cooler serialization design method for air compressor air inlet pretreatment - Google Patents
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- 238000013461 design Methods 0.000 title claims abstract description 18
- 238000000034 method Methods 0.000 title claims abstract description 18
- 239000012530 fluid Substances 0.000 claims abstract description 30
- 238000001816 cooling Methods 0.000 claims abstract description 14
- 238000012795 verification Methods 0.000 claims abstract description 4
- 239000010949 copper Substances 0.000 claims description 36
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 32
- 229910052802 copper Inorganic materials 0.000 claims description 32
- 238000004364 calculation method Methods 0.000 claims description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 9
- 229910052782 aluminium Inorganic materials 0.000 claims description 6
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 6
- 241001417523 Plesiopidae Species 0.000 claims description 3
- 238000000926 separation method Methods 0.000 claims description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 11
- 239000007789 gas Substances 0.000 description 9
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 239000004753 textile Substances 0.000 description 4
- 238000005265 energy consumption Methods 0.000 description 3
- 238000009987 spinning Methods 0.000 description 3
- 239000011324 bead Substances 0.000 description 2
- 239000010725 compressor oil Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 108010074506 Transfer Factor Proteins 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- -1 greasy dirt Substances 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 231100000956 nontoxicity Toxicity 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/06—Power analysis or power optimisation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
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Abstract
The invention discloses a surface cooler serialization design method for air compressor inlet pretreatment, which specifically comprises the following steps: according to the air yield G of the air compressor, calculating the cooling capacity Q of the surface cooler: determining parameters of a coil pipe of the surface cooler according to the cooling capacity Q of the surface cooler; calculating the total heat efficiency E 'achieved by the surface cooler according to the gas yield G, the coil parameters of the surface cooler, the air parameters and the fluid parameters' g And utilizes the required total heat efficiency E g Total heat efficiency E 'achieved for the surface cooler' g And (5) performing verification. Under the condition of not changing the original equipment, according to the change of the gas production amount caused by the difference of the model numbers of the air compressors, the air quality can be ensured to meet the requirements of the temperature, the humidity and the pressure of the air intake of the air compressors by changing the size and the specification of the cooling equipment; the surface cooler suitable for the air compressors with different gas production rates can be quickly designed, and the design and manufacturing cost is reduced.
Description
Technical Field
The invention belongs to the technical field of heat exchange equipment design methods, and relates to a surface cooler serialization design method for air compressor air inlet pretreatment.
Background
The air source of the air compressor is from the atmosphere, and is used as a power source, and the air compressor has the characteristics of no toxicity, no harm, safety, compressibility, convenient taking and the like. Compressed air is called the fourth utility and plays an important role in modern society. The compressed air accounts for about 10% of the total energy used in the current industry, and the air compressor is widely applied to air compression systems in the textile industry, and the energy consumption of the air compression systems in the textile industry accounts for more than 30% of the whole energy consumption. The China is used as a spinning large country, 70% of the spinning industry is distributed in the areas of China such as long triangles and bead triangles, and the high-temperature and high-humidity areas of China in the bead triangle places account for about half of the year. Therefore, the method aims at high-temperature and high-humidity areas, reduces the energy consumption of the air compressor, optimizes energy conservation, and has important significance for energy conservation and yield reduction advocated by China and promotion of sustainable development of energy sources.
The air compressor is a device for compressing air, is a main device of an air compression station, and is used for conveying high-pressure air for various air utilization systems of textile factories so as to meet the demands of users. Air is a mixture of gases. Various solid substances such as water vapor, greasy dirt, metal powder, rust mud and the like exist in the air.
The air compressor has higher air suction temperature, and firstly, the pressure is easily brought to a cooling system to influence the cooling effect, so that the temperature of the generated air can not reach an ideal value, and the high temperature of the air compressor is caused. Secondly, the high air suction temperature of the air compressor can also reduce the compression ratio of the air compressor, influence the gas yield of compressed air, influence gas-end equipment and waste power energy sources such as electric energy. And thirdly, the service life of the air compressor oil is easily influenced due to high air suction temperature of the air compressor, the frequency of air compressor oil replacement is increased, and additional loss is caused. In the spinning mill air compression station, the main sources of compressed air in the air compression system are two, namely, the air is directly taken in the air compression station to compress, and the outdoor air outside the air compression station is taken to compress. Most textile factories simply filter, remove dust and mute the introduced air, do not consider the pretreatment of temperature and humidity of the introduced air, and do not relate to a method for designing pretreatment equipment aiming at different air production rates of the air compressor, and if the pretreatment equipment of the air compressor is unsuitable, the working efficiency of the air compressor is also reduced.
Disclosure of Invention
The invention aims to provide a surface air cooler serialization design method for air compressor air inlet pretreatment, which can improve the working efficiency of an air compressor.
The technical scheme adopted by the invention is that the surface cooler serialization design method for air compressor air inlet pretreatment specifically comprises the following steps:
step 1, calculating the cooling capacity Q of the surface cooler according to the air yield G of the air compressor:
Q＝G m ·(h 1 -h 2 )
in the above, h 1 Specific enthalpy of inlet air, h 2 For the specific enthalpy of the air out of the air conditioner,ρ m is air density;
step 2, determining parameters of coils of the surface cooler according to the cooling capacity Q of the surface cooler;
step 3, calculating total heat efficiency E 'achieved by the surface cooler according to the gas yield G, the coil parameters, the air parameters and the fluid parameters of the surface cooler' g And utilizes the required total heat efficiency E g Total heat efficiency E 'achieved for the surface cooler' g And (5) performing verification.
The invention is also characterized in that:
the parameters of the surface cooler coil include: copper pipe outer diameter d 0 Inner diameter d of copper pipe i Wall thickness delta of copper pipe and hole pitch S of copper pipe 1 Row spacing S of copper tubes 2 Fin thickness delta f Fin number N per inch f Half wavelength X of corrugated fin f Wave height P of corrugated fin d Number of holes N 1 Number of rows N 2 Length L of windward side of copper pipe 0 Form L of loop s Diameter d of fin root b Fin spacing S f Through-flow cross-sectional area f of surface cooler w Surface area f of outer fin of copper tube with length of each meter f Total external surface area f per meter of tube length 0 External surface area f of base tube between long fins of each meter tube b 。
The specific steps of the step 3 are as follows:
step 3.1, calculating the heat exchange area F of the surface cooler:
F＝a·N 2 ·F y
wherein a is the Rib coefficient, F y The windward area of the surface cooler;
step 3.2, calculating the total heat exchange coefficient K of the surface cooler s ：
In the above formula, ζ is the humidity separation coefficient of the surface cooler, τ is the ribbing coefficient, and r=s 1 /2，r 0 Is the outer radius of copper pipe lambda Copper (Cu) Is the heat conductivity coefficient of copper, lambda Aluminum (Al) Is the heat conductivity coefficient of aluminum, alpha w Is the heat exchange coefficient of the fluid side of the surface cooler, alpha a The heat exchange coefficient of the air side of the surface cooler;
step 3.3, calculating the total heat efficiency E 'achieved by the surface cooler' g Total heat efficiency E 'achieved by the surface cooler' g And the required total heat efficiency E g The difference value of the temperature difference is less than 0.001, the verification is completed, and the total heat efficiency E 'which can be achieved by the surface cooler is achieved' g And the required total thermal efficiency E g The calculation method of (2) is as follows:
in the above, c p Is the constant pressure specific heat capacity of air, t 1 Air inlet temperature t of surface cooler w1 Is the temperature t of water inlet w2 At the outlet water temperature t 2 Is the air outlet temperature.
The heat exchange coefficient alpha of the air side of the surface cooler in the step 3.2 a The calculation formula of (2) is as follows:
α a ＝j·G ρ ·(1000c p )·Pr -2/3
v max ＝v y /ε
in the above, pr is an air state parameter, G ρ And epsilon is the net surface ratio of the surface cooler.
Step (a)3.2 the heat exchange coefficient alpha of the fluid side of the surface cooler w The calculation formula of (2) is as follows:
in the above, ρ w For fluid density in the tube, W is fluid flow in the tube, c w Lambda is the specific heat capacity of the fluid w Is the coefficient of thermal conductivity of the fluid.
The beneficial effects of the invention are as follows:
according to the surface cooler serialization design method for air compressor air inlet pretreatment, the pretreated surface cooler is arranged in front of the air compressor, so that the temperature and humidity of air at the inlet of the air compressor can be reduced, the air inlet pressure can be increased, the air suction amount of the air compressor is increased, the power consumption is obviously reduced, and the power is reduced; under the condition of not changing the original equipment, according to the change of the gas production amount caused by the difference of the model numbers of the air compressors, the air quality can be ensured to meet the temperature, humidity and pressure requirements of the air intake of the air compressors by changing the size and specification of the cooling equipment, so that the working efficiency of the air compressors is improved; the surface cooler suitable for the air compressors with different gas production rates can be quickly designed, and the design and manufacturing cost is reduced.
Drawings
FIG. 1 is a schematic diagram of a pretreatment device in a surface cooler serialization design method for pretreatment of air intake of an air compressor;
fig. 2 is a schematic diagram of dimension parameters of a surface cooler obtained by a surface cooler serialization design method for air compressor inlet pretreatment.
In the figure, a surface cooler 1, a filter 2, an air compressor 3, an air inlet air pipe 4, an outlet air pipe 5 and a hose 6.
Detailed Description
The invention will be described in detail below with reference to the drawings and the detailed description.
The invention relates to a surface cooler serialization design method for air compressor air inlet pretreatment, wherein the related air compressor air inlet pretreatment equipment, as shown in figure 1, comprises a surface cooler 1, wherein the air inlet end of the surface cooler 1 is connected with a filter 2 through an air inlet air pipe 4, the air outlet end of the surface cooler 1 is connected with an air compressor 3 through an outlet air pipe 5, and the outlet air pipe 5 is connected with the air inlet of the air compressor 3 through an air inlet hose 6.
The invention discloses a surface cooler serialization design method for air compressor inlet pretreatment, which specifically comprises the following steps:
step 1, according to the air yield G of the air compressor, the air yield G of the embodiment is 130-160m 3 Per min, i.e. g=9600 m 3 And (h) calculating the cooling capacity Q of the surface cooler:
Q＝G m ·(h 1 -h 2 )
in the above, h 1 Specific enthalpy of inlet air, h 2 For the specific enthalpy of the air out of the air conditioner,ρ q is air density;
in this example, gm=3.10 kg/s, ρ q ＝1.161kg/m3，h 1 ＝107.19kJ/kg；h 2 =83.93 kJ/kg; calculating to obtain the cooling capacity Q=72.02 kW of the surface cooler;
step 2, determining parameters of coils of the surface cooler according to the cooling capacity Q of the surface cooler;
the coil parameters include: copper pipe outer diameter d 0 Inner diameter d of copper pipe i Wall thickness delta of copper pipe and hole pitch S of copper pipe 1 Row spacing S of copper tubes 2 Fin thickness delta f Fin number N per inch f Half wavelength X of corrugated fin f Wave height P of corrugated fin d Number of holes N 1 Number of rows N 2 Length L of windward side of copper pipe 0 Form L of loop s Diameter d of fin root b Fin spacing S f Through-flow cross-sectional area f of surface cooler w Surface area f of outer fin of copper tube with length of each meter f Total external surface area f per meter of tube length 0 External surface area f of base tube between long fins of each meter tube b ；
In this example, as shown in FIG. 2, the parameters of the selected surface cooler coil are as follows:
d 0 ＝15.88mm，d i ＝14.96mm，δ＝0.46mm，S 1 ＝38mm，S 2 ＝33mm，δ f ＝0.115mm，N f 12 pieces, X f ＝8.25mm，P d ＝2mm，N 1 =23, N 2 Row=4, L 0 ＝1200mm，L s Loop=1, f f ＝0.99m 2 /m，f 0 ＝1.04m 2 /m，f b ＝0.048m 2 /m，f w ＝0.004m 2 ，d b ＝16.11mm，S f ＝2.12mm；
Step 3, calculating the total heat efficiency E 'achieved by the surface cooler according to the gas yield G, the coil parameters of the surface cooler, the air parameters and the fluid parameters' g Utilizing the required total heat efficiency E g Total heat efficiency E 'achieved by surface cooler' g And (3) verifying, if the difference value of the two is smaller than 0.001, proving that the surface air cooler can meet the air inlet pretreatment requirement of the air compressor.
Step 3.1, calculating the heat exchange area F of the surface cooler:
F＝a·N 2 ·F y
in the above formula, a is the rib-pass coefficient, a=27.37, f y F is calculated for the windward area of the surface cooler y ＝1.05m 2 ，F＝114.83m 2 。
Step 3.2, calculating the total heat exchange of the surface coolerCoefficient K s ：
ζ is the humidity separation coefficient of the surface cooler, ζ=2.88, τ is the ribbing coefficient, τ=22.13, φ 0 For rib surface full efficiency, r=s 1 /2，，r 0 Is the outer radius of copper pipe lambda Copper (Cu) Is the heat conductivity coefficient of copper, lambda Copper (Cu) ＝398W/(m·℃)，λ Aluminum (Al) For the heat conductivity coefficient of aluminum, eta is calculated f For fin efficiency, eta f ＝0.418，m 2 Is the shape parameter of the fin, m 2 ＝141.931，l e For fin equivalent height, l e ＝0.017m；
Calculating heat exchange coefficient alpha of air side of surface cooler a ：
α a ＝j·G ρ ·(1000c p )·Pr -2/3
ν max ＝v y /ε
In the above, c p C is the constant pressure specific heat capacity of air p =1.005 kJ/(kg·deg.c), pr is an air state parameter, pr=0.70, g ρ For air mass flow rate, G ρ ＝2.95kg/(m 2 S), ε is the net surface ratio of the surface cooler, ε=0.54, calculated, re q Re is the air Reynolds number at the minimum air flow cell q ＝1069.98，v max Wind speed v being the minimum air flow cell max ＝4.67m/s，d e Equivalent diameter d of minimum air flow cell e ＝00037m，v y Is the face wind speed of the surface cooler, v y =2.54 m/s, j fin heat transfer factor, j=0.022;
calculating heat exchange coefficient alpha of fluid side of surface cooler w ：
In the above, ρ w For fluid density in the tube ρ w ＝998.01kg/m 3 W is the flow of fluid in the tube, w= 206.75L/min, c w C is the specific heat capacity of the fluid w ＝4.18kJ/(kg·℃)，λ w Is the coefficient of thermal conductivity of fluid lambda w =0.60W/(m· ℃) and ψ is the physical coefficient, ψ= 1833.48, calculated, v w For fluid flow velocity in the tube, v w ＝0.85m/s，α w ＝3745.14W/(m 2 ·℃)；
Step 3.3, calculating the total heat efficiency E 'achieved by the surface cooler' g Total heat efficiency E 'achieved by the surface cooler' g And the required total heat efficiency E g The difference value of (2) is less than 0.001, and the total heat efficiency E 'achieved by the surface cooler is' g And the required total thermal efficiency E g The calculation method of (2) is as follows:
in the above, t 1 Air inlet temperature t of surface cooler w1 Is the temperature t of water inlet w2 At the outlet water temperature t 2 For the air outlet temperature, it is calculated that β is the number of heat transfer units, β=0.83, γ is the water equivalent ratio, γ=0.62, e' g ＝0.4742，E g 0.4735, which differ by less than 0.001, the surface cooler of the present embodiment conforms to the intake air amount g=9600m 3 And/h, the requirement of an air compressor.
The invention also relates to the determination of the air side pressure of a surface coolerDecreasing Δp a And a fluid side pressure drop Δp w Calculation is performed according to the air side pressure drop Δp a And a fluid side pressure drop Δp w The water pump with corresponding specification is selected to overcome the resistance of the fluid in the pipeline, and the calculation method is as follows:
Δp a ＝Δp a1 +Δp a2 ；
in the above, mu 1 Is the friction coefficient, mu, of air flowing through the fins 1 ＝0.064；μ 2 Is the local resistance coefficient, mu, of air flowing through the tube bundle 2 ＝5.315；Δp a1 For the pressure drop, Δp, caused by friction of air flowing through the fins a1 ＝29.126Pa；Δp a2 Is the local pressure drop, Δp, of air as it flows through the tube bundle a2 ＝67.217Pa；Δp a Δp is the air side pressure drop of the surface cooler a =96.34 Pa; b is the length of the surface cooler along the airflow direction, b=132 mm;
pressure drop deltap of fluid side of surface cooler w ：
Re w Re, the Reynolds number of the fluid inside the tube w ＝12827.53；λ f Is the coefficient of resistance of the fluid side path lambda f =0.030; z is the number of bends, taking z=46; lambda (lambda) m1 Taking lambda as the local resistance coefficient of the elbow m1 ＝0.5；λ m2 Is the friction resistance coefficient of the elbow lambda m2 ＝0.120；d i Is the inner diameter of copper pipe d i ＝14.96mm；Δp wf Pressure drop Δp due to resistance along the fluid side wf ＝3471.82Pa；Δp wm Pressure drop Δp for local resistance on the body side wm = 15554.52Pa; pressure drop deltap of fluid side of surface cooler w ＝19.03kPa。
According to the method, the invention also designs the surface cooler with different gas production rates of the air compressor, and the specific parameters are as follows:
through the mode, the surface cooler serial design method for the air compressor air inlet pretreatment can reduce the temperature and humidity of air at the inlet of the air compressor and increase the air inlet pressure by arranging the pretreated surface cooler in front of the air compressor, so that the air suction amount of the air compressor is increased, the power consumption is obviously reduced, and the power is reduced; under the condition of not changing the original equipment, according to the change of the gas production amount caused by the difference of the model numbers of the air compressors, the air quality can be ensured to meet the temperature, humidity and pressure requirements of the air intake of the air compressors by changing the size and specification of the cooling equipment; the surface cooler suitable for the air compressors with different gas production rates can be quickly designed, and the design and manufacturing cost is reduced.
Claims (2)
1. The surface cooler serialization design method for air compressor inlet pretreatment is characterized by comprising the following steps:
step 1, calculating the cooling capacity Q of the surface cooler according to the air yield G of the air compressor:
Q＝G m ·(h 1 -h 2 )
in the above, h 1 Specific enthalpy of inlet air, h 2 For the specific enthalpy of the air out of the air conditioner,ρ m is air density;
step 2, determining parameters of coils of the surface cooler according to the cooling capacity Q of the surface cooler;
step 3, calculating total heat efficiency E 'achieved by the surface cooler according to the gas yield G, the coil parameters, the air parameters and the fluid parameters of the surface cooler' g And utilizes the required total heat efficiency E g Total heat efficiency E 'achieved for the surface cooler' g Verifying;
the specific steps of the step 3 are as follows:
step 3.1, calculating the heat exchange area F of the surface cooler:
F＝a·N 2 ·F y
wherein a is the Rib coefficient, F y The windward area of the surface cooler;
step 3.2, calculating the total heat exchange coefficient K of the surface cooler s ：
In the above formula, ζ is the humidity separation coefficient of the surface cooler, τ is the ribbing coefficient, and r=s 1 /2，r 0 Is the outer radius of copper pipe lambda Copper (Cu) Is the heat conductivity coefficient of copper, lambda Aluminum (Al) Is the heat conductivity coefficient of aluminum, alpha w Is the heat exchange coefficient of the fluid side of the surface cooler, alpha a The heat exchange coefficient of the air side of the surface cooler;
step 3.3, calculating the total heat efficiency E 'achieved by the surface cooler' g Total heat efficiency E 'achieved by the surface cooler' g And the required total heat efficiency E g The difference value of the temperature difference is less than 0.001, the verification is completed, and the total heat efficiency E 'which can be achieved by the surface cooler is achieved' g And the required total thermal efficiency E g The calculation method of (2) is as follows:
in the above, c p Is the constant pressure specific heat capacity of air, t 1 Air inlet temperature t of surface cooler w1 Is the temperature t of water inlet w2 At the outlet water temperature t 2 Is the air outlet temperature;
the heat exchange coefficient alpha of the air side of the surface cooler in the step 3.2 a The calculation formula of (2) is as follows:
α a ＝j·G ρ ·(1000c p )·Pr -2/3
v max ＝v y /ε
in the above, pr is an air state parameter, G ρ Air mass flow rate, epsilon is the net surface ratio of the surface cooler;
the surface cooler coil parameters include: copper pipe outer diameter d 0 Inner diameter d of copper pipe i Wall thickness delta of copper pipe and hole pitch S of copper pipe 1 Row spacing S of copper tubes 2 Fin thickness delta f Fin number N per inch f Half wavelength X of corrugated fin f Wave height P of corrugated fin d Number of holes N 1 Number of rows N 2 Length L of windward side of copper pipe 0 Form L of loop s Diameter d of fin root b Fin spacing S f Through-flow cross-sectional area f of surface cooler w Surface area f of outer fin of copper tube with length of each meter f Total external surface area f per meter of tube length 0 External surface area f of base tube between long fins of each meter tube b 。
2. The method for designing a surface cooler for air compressor intake pretreatment of claim 1, wherein the surface cooler fluid side heat exchange coefficient α in step 3.2 w The calculation formula of (2) is as follows:
in the above, ρ w For fluid density in the tube, W is fluid flow in the tube, c w Lambda is the specific heat capacity of the fluid w Is the coefficient of thermal conductivity of the fluid.
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