CN112066742A - Optimization method for utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation - Google Patents
Optimization method for utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation Download PDFInfo
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- 239000002918 waste heat Substances 0.000 title claims abstract description 81
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 title claims abstract description 70
- 239000003546 flue gas Substances 0.000 title claims abstract description 70
- 238000010248 power generation Methods 0.000 title claims abstract description 34
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000011521 glass Substances 0.000 title claims abstract description 18
- 238000005457 optimization Methods 0.000 title abstract description 6
- 238000004364 calculation method Methods 0.000 claims abstract description 35
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 29
- 238000004519 manufacturing process Methods 0.000 claims abstract description 10
- 239000000779 smoke Substances 0.000 claims description 13
- 238000001704 evaporation Methods 0.000 claims description 8
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- 238000000605 extraction Methods 0.000 claims description 8
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims description 7
- 239000001301 oxygen Substances 0.000 claims description 7
- 229910052760 oxygen Inorganic materials 0.000 claims description 7
- 239000003245 coal Substances 0.000 claims description 6
- 238000004321 preservation Methods 0.000 claims description 6
- 239000002253 acid Substances 0.000 claims description 5
- 239000007789 gas Substances 0.000 claims description 5
- 229920006395 saturated elastomer Polymers 0.000 claims description 4
- NAWXUBYGYWOOIX-SFHVURJKSA-N (2s)-2-[[4-[2-(2,4-diaminoquinazolin-6-yl)ethyl]benzoyl]amino]-4-methylidenepentanedioic acid Chemical compound C1=CC2=NC(N)=NC(N)=C2C=C1CCC1=CC=C(C(=O)N[C@@H](CC(=C)C(O)=O)C(O)=O)C=C1 NAWXUBYGYWOOIX-SFHVURJKSA-N 0.000 claims description 3
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- 238000002844 melting Methods 0.000 description 4
- 230000008018 melting Effects 0.000 description 4
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- 238000012986 modification Methods 0.000 description 3
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- 238000009413 insulation Methods 0.000 description 2
- 239000012774 insulation material Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000004064 recycling Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003034 coal gas Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000012821 model calculation Methods 0.000 description 1
- 239000006060 molten glass Substances 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F27—FURNACES; KILNS; OVENS; RETORTS
- F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
- F27D17/00—Arrangements for using waste heat; Arrangements for using, or disposing of, waste gases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
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- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
- F22B33/18—Combinations of steam boilers with other apparatus
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Abstract
The invention discloses an optimization method for utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation, which comprises the following steps of: a. calculating the steam production of the waste heat boiler, b, calculating the pressure loss and the temperature loss of water supply and steam, c, calculating the power generation capacity of the steam turbine, d, judging whether the power generation power of the steam turbine is the maximum value or not, and if so, outputting a waste heat boiler result parameter, a steam turbine result parameter and a pipe network result parameter; if not, adjusting and adjusting the set steam inlet pressure of the steam turbine and repeating the calculation of the steps a, b and c; the invention provides a system optimization method, which can calculate the generated energy according to the flue gas parameters and the heat supply demand, adjust the steam pressure to obtain the maximum generated energy, and adjust the operation parameters according to the change of the flue gas parameters in the actual operation.
Description
Technical Field
The invention relates to the technical field of glass kiln flue gas waste heat utilization, in particular to a method for optimizing the utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation.
Background
Fuels such as heavy oil, natural gas and coal gas are used in the glass kiln production, and the fuels are combusted in the furnace to release heat, wherein the heat absorption of the molten glass accounts for 35-40% of the total heat; the heat dissipation loss through the surface of the melting furnace is 20-25%; the smoke discharge loss is 30-40%. A large amount of heat is taken away by the glass melting furnace flue gas, and flue gas waste heat power generation is an effective mode for recycling the waste heat of the glass melting furnace flue gas, so that the recycling rate of primary energy can be improved, and the heat pollution to the environment caused by the waste heat can be reduced.
The parameters of the waste heat power generation system determine whether the waste heat utilization and the generated energy utilization can be maximized, so that how to obtain the optimal parameters of the waste heat power generation system is the problem to be solved.
Disclosure of Invention
The invention aims to provide a method for optimizing the utilization of the waste heat and the generated energy of the glass kiln flue gas waste heat power generation.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation comprises the following steps:
a. the steam production of the waste heat boiler is calculated,
a1, firstly, calculating an acid dew point to obtain the exhaust gas temperature of the waste heat boiler; and then calculating the enthalpy value data of each component of the flue gas to obtain enthalpy thermometers of a superheat section, a denitration system empty tube box, an evaporation section, a coal saving section and an oxygen removal evaporation section of the waste heat boiler, wherein the enthalpy value of each section of the flue gas of the waste heat boiler is calculated according to a formula (1):
Qi＝Gi[∑miIi+(ai-1)Ica] (1)
q in formula (1)iIs the total enthalpy value G of the flue gas at a certain temperatureiAs the flue gas flow rate at this temperature, miIs the mole percentage of a certain component, IiTo the enthalpy of the corresponding component at that temperature, IcaIs the enthalpy of air at that temperature, aiThe air leakage rate is relative to the inlet of the waste heat boiler at the temperature;
a2, determining the flue gas temperature of each section of the waste heat boiler as follows:
superheater inlet temperature T1Superheater outlet/evaporator inlet temperature T2Evaporator outlet/economizer inlet temperature T3Temperature T at the exit of economizer/inlet of deaerator4Inlet/exhaust temperature T of oxygen removal evaporator5；
T1The inlet flue gas temperature of the waste heat boiler;
by the formula Q1-Q2＝M·(h1-h2) (2) calculating the smoke at T2The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer2(ii) a Wherein Q1、h1The total enthalpy value of the flue gas, the enthalpy value of the working medium and Q of the inlet of the superheater are respectively2、h2The total enthalpy value of the flue gas at the outlet of the superheater and the enthalpy value of the working medium are respectively, and M is the flow of the working medium, namely the steam production of the waste heat boiler;
T3steam drum saturation temperature + narrow point temperature difference
By the formula Q3-Q4M (1+ blowdown rate) · (h)3-h4) (3) calculating the smoke at T4The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer4(ii) a Wherein Q3、h4The total enthalpy value of the smoke gas, the enthalpy value of the working medium and Q of the inlet of the coal economizer respectively2、h2The total enthalpy value of the smoke at the outlet of the economizer and the enthalpy value of the working medium are respectively;
m is calculated according to equation (4):
M＝(Q1-Q3)/(h1-h3) + blowdown rate (h)3’-h3) Wherein h is3' is the saturated hydrothermal enthalpy value of the steam drum; the calculation of M and T2The calculation of (2) is a loop iteration calculation;
judging whether the narrow point temperature difference meets the requirement, and if so, keeping calculation for standby; if not, adjusting the steam inlet pressure of the steam turbine which is adjusted and set, and repeating the step a2 to calculate;
b. calculating the pressure loss and the temperature loss of the feed water and the steam,
b1, calculating the pressure loss delta p of the pipe network according to the formula (5),
in the formula (5)
Is the friction coefficient of the pipeline, L is the length of the pipeline, zeta is the local resistance coefficient, ν is the medium flow rate, g is the gravitational acceleration;
the temperature loss and the heat preservation thickness of the pipe network are calculated according to the formulas (6) and (7),
d in the formulae (6) and (7)0Is the outside diameter of the pipe, D1The outer diameter of the heat preservation layer is the heat preservation thickness,gamma is heat conductivity of heat insulating material, KrC is the specific heat capacity of the medium, TAAnd TBRespectively, the medium temperature at the starting point and the end point of the pipeline, TaThe temperature is the ambient temperature, and alpha is the surface heat transfer coefficient of the outer surface of the insulating layer to the atmosphere;
judging whether the pressure loss and the temperature loss exceed set values, if so, adjusting the pipe network parameters to repeat the calculation of b1, and if not, performing the step b 2;
b2, calculating the mixed steam temperature of the steam of each waste heat boiler in front of the steam turbine,
first pass through
Calculating to obtain enthalpy value of mixed steam, and determining T according to steam propertyMixing of；
c. Calculating the power generation capacity of the steam turbine,
the generated power N of the steam turbine is calculated according to the formula (9):
N＝ηη1η2[MintohInto-(MInto-MDrawer)-MDrawerhDrawer]/3600 (9)，
Eta, eta in formula (9)1Relative internal efficiency, mechanical efficiency, eta, of the steam turbine, respectively2For generator efficiency, MIntoIs the steam inlet volume, h, of the steam turbineIntoIs the enthalpy of the inlet steam of the turbine, hRow boardFor the exhaust enthalpy of the turbine, NDecrease in the thickness of the steelFor power loss, MDrawerThe amount of extracted steam is hDrawerIs the enthalpy of the extracted steam;
the air extraction amount is calculated according to the formula (10),
m in formula (10)DrawerFor the amount of extracted steam, MFor supplying toFor the required heat supply, hDrawerIs the enthalpy of the extraction, hFor supplying toFor supplying enthalpy of steam or hot water, hReducingIs the enthalpy of the desuperheated water;
d. judging whether the power generation power of the steam turbine is the maximum value, and if so, outputting a waste heat boiler result parameter, a steam turbine result parameter and a pipe network result parameter; if the steam turbine inlet pressure is not the maximum value, adjusting the steam turbine inlet pressure which is adjusted and set, and repeating the steps a, b and c.
Preferably, step c further comprises calculating the motor running power of the waste heat power generation auxiliary machine,
the operating power of the fan is according to the formula
The calculation is carried out according to the calculation,
the running power of the water pump is according to the formula
The calculation is carried out according to the calculation,
q in the formulae (11) and (12)vIs volume flow, p is fan full pressure, ρ is fluid density, H is pump head, ηGeneral assembly、ηtm、ηgThe total efficiency, prime mover efficiency, and transmission efficiency of the pump and fan, respectively; and d, outputting the result parameters of the auxiliary equipment of the waste heat power station after judging that the power generation power of the steam turbine is the maximum value.
The invention has the beneficial effects that in order to maximally utilize the waste heat of the flue gas of the glass kiln, provide power for the outside and provide steam or hot water required by production and life, the invention provides a system optimization method, which not only can calculate the generated energy according to the flue gas parameters and the heat supply requirement, but also can adjust the steam pressure to obtain the maximized generated energy, and can adjust the operation parameters according to the change of the flue gas parameters in actual operation to tailor the flue gas parameters to measure and tailor the flue gas parameters, and unconditionally adapt to the flue gas parameters discharged by the glass melting kiln, thereby achieving the purpose of 'how much and how much to eat'.
Drawings
The invention is further illustrated with reference to the following figures and examples:
FIG. 1 is a schematic diagram of the optimization process of the present invention.
Detailed Description
As shown in FIG. 1, the invention provides a method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation, which comprises the following steps:
a. passing through the parameters of the glass kiln flue gas: flue gas flow, temperature and components, constructing an enthalpy and temperature meter model of the waste heat boiler, calculating the residual heat quantity of the flue gas, and combining the constructed waste heat boiler steam-water heat balance model to further calculate the steam yield;
when the calculation of the available residual heat quantity and the steam yield of the flue gas is carried out:
firstly, reading the flow rate, temperature and components of the flue gas as basic data, and calculating the acid dew point temperature according to the components to obtain the temperature of the flue gas, wherein other set conditions comprise set temperature difference of an approach point of a waste heat boiler, air leakage rate and temperature drop of a denitration system (if the flue gas denitration system is matched);
calculating enthalpy temperature meters of a superheat section of the waste heat boiler, a denitration system empty tube box (if any), an evaporation section, a coal saving section and an oxygen removal evaporation section according to enthalpy value data of each component of the flue gas;
calculating the heat exchange quantity of the flue gas and the steam of each heat exchange section of the waste heat boiler according to the set steam pressure and temperature parameters through a steam-water heat balance model, and calculating to obtain the steam yield;
b. according to actual water supply and steam pipe network data (pipe diameter, length, heat preservation thickness and performance), a pipe network temperature and pressure loss model is constructed, and pressure loss, temperature loss and flow loss of water supply and steam are calculated;
when calculating the pressure loss and temperature loss of the feedwater and steam:
firstly, reading parameters of water supply and steam, and calculating an economical and reasonable pipeline specification, pressure loss, temperature loss and flow loss of a water supply and steam pipe network according to the actual length of the pipe network and the performance of a heat insulation material, so as to obtain steam parameters of an inlet of a steam turbine;
c. calculating the power generation power of the steam turbine according to the steam parameters and the actual data of the operation of the glass kiln waste heat power station;
when calculating the power generation power of the steam turbine:
reading the actual steam inlet pressure, temperature and flow of the steam turbine, setting steam extraction parameters according to the heat supply requirement of a plant area, and calculating the final power generation power of the steam turbine;
d. judging whether the power generation power of the steam turbine is the maximum value, and if so, outputting a waste heat boiler result parameter, a steam turbine result parameter and a pipe network result parameter; if the steam turbine inlet pressure is not the maximum value, adjusting the steam turbine inlet pressure which is adjusted and set, and repeating the steps a, b and c.
And (c) constructing constraint conditions according to the flue gas acid dew point temperature, the waste heat boiler narrow point temperature difference and the temperature difference of steam at the outlet of the waste heat boiler before and after temperature reduction in the calculation formulas of the steps a, b and c.
The mode for calculating the maximization of the generating power of the steam turbine is as follows:
and (3) giving an initial value of steam pressure at the inlet of the steam turbine, and repeating all model calculation processes until the power generation power of the steam turbine and the corresponding value of the steam pressure at the inlet of the steam turbine are obtained, wherein all constraint conditions must be met in the calculation process.
And according to the calculation result, calculating the motor running power of the main waste heat power generation auxiliary machines (an induced draft fan, various pumps, a cooling tower and the like) so as to determine the installed power of each auxiliary machine.
For a more clear illustration of the invention, a more detailed solution is now provided:
a method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation comprises the following steps:
a. the steam production of the waste heat boiler is calculated,
a1, firstly, calculating an acid dew point to obtain the exhaust gas temperature of the waste heat boiler; and then calculating the enthalpy value data of each component of the flue gas to obtain enthalpy thermometers of a superheat section, a denitration system empty tube box, an evaporation section, a coal saving section and an oxygen removal evaporation section of the waste heat boiler, wherein the enthalpy value of each section of the flue gas of the waste heat boiler is calculated according to a formula (1):
Qi＝Gi[∑miIi+(ai-1)Ica] (1)
q in formula (1)iIs the total enthalpy value G of the flue gas at a certain temperatureiAs the flue gas flow rate at this temperature, miIs the mole percentage of a certain component, IiTo the enthalpy of the corresponding component at that temperature, IcaIs the enthalpy of air at that temperature, aiThe air leakage rate is relative to the inlet of the waste heat boiler at the temperature;
a2, determining the flue gas temperature of each section of the waste heat boiler as follows:
superheater inlet temperature T1Superheater outlet/evaporator inlet temperature T2Evaporator outlet/economizer inlet temperature T3Temperature T at the exit of economizer/inlet of deaerator4Inlet/exhaust temperature T of oxygen removal evaporator5；
T1The inlet flue gas temperature of the waste heat boiler;
by the formula Q1-Q2＝M·(h1-h2) (2) calculating the smoke at T2The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer2(ii) a Wherein Q1、h1The total enthalpy value of the flue gas, the enthalpy value of the working medium and Q of the inlet of the superheater are respectively2、h2The total enthalpy value of the flue gas at the outlet of the superheater and the enthalpy value of the working medium are respectively, and M is the flow of the working medium, namely the steam production of the waste heat boiler;
T3steam drum saturation temperature + narrow point temperature difference
By the formula Q3-Q4M (1+ blowdown rate) · (h)3-h4) (3) calculating the smoke at T4The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer4(ii) a Wherein Q3、h4The total enthalpy value of the smoke gas, the enthalpy value of the working medium and Q of the inlet of the coal economizer respectively2、h2The total enthalpy value of the smoke at the outlet of the economizer and the enthalpy value of the working medium are respectively;
m is calculated according to equation (4):
M＝(Q1-Q3)/(h1-h3) + blowdown rate (h)3’-h3) Wherein h is3' is the saturated hydrothermal enthalpy value of the steam drum; the calculation of M and T2The calculation of (2) is a loop iteration calculation;
judging whether the narrow point temperature difference meets the requirement, and if so, keeping calculation for standby; if not, adjusting the steam inlet pressure of the steam turbine which is adjusted and set, and repeating the step a2 to calculate;
b. calculating the pressure loss and the temperature loss of the feed water and the steam,
b1, calculating the pressure loss delta p of the pipe network according to the formula (5),
in the formula (5)
Is the friction coefficient of the pipeline, L is the length of the pipeline, zeta is the local resistance coefficient, ν is the medium flow rate, g is the gravitational acceleration;
the temperature loss and the heat preservation thickness of the pipe network are calculated according to the formulas (6) and (7),
d in the formulae (6) and (7)0Is the outside diameter of the pipe, D1The outer diameter of the heat-insulating layer is the heat-insulating thickness, gamma is the heat conductivity of the heat-insulating material, KrC is the specific heat capacity of the medium, TAAnd TBRespectively, the medium temperature at the starting point and the end point of the pipeline, TaThe temperature is the ambient temperature, and alpha is the surface heat transfer coefficient of the outer surface of the insulating layer to the atmosphere;
judging whether the pressure loss and the temperature loss exceed set values, if so, adjusting the pipe network parameters to repeat the calculation of b1, and if not, performing the step b 2; specifically, if the calculation result shows that the pressure loss is too large, the pipe diameter can be increased; if the calculation result shows that the temperature loss is too large, increasing the heat insulation thickness or changing the type of the heat insulation material;
when there are 2 or more than quantity exhaust-heat boiler, still need calculate each exhaust-heat boiler pressure loss and temperature loss, each exhaust-heat boiler export steam pressure value's formula of calculating is:
p1-Δp1＝p2-Δp2＝pi-Δpi＝pinto+ Δ p', where pInto+ delta p' is the pressure loss of the mixed steam of each waste heat boiler before the steam turbine inlet;
b2, calculating the mixed steam temperature of the steam of each waste heat boiler in front of the steam turbine,
first pass through
Calculating to obtain enthalpy value of mixed steam, and determining T according to steam propertyMixing of；
c. Calculating the power generation capacity of the steam turbine,
the generated power N of the steam turbine is calculated according to the formula (9):
N＝ηη1η2[MintohInto-(MInto-MDrawer)-MDrawerhDrawer]/3600 (9)，
Eta, eta in formula (9)1Relative internal efficiency, mechanical efficiency, eta, of the steam turbine, respectively2For generator efficiency, MIntoIs the steam inlet volume, h, of the steam turbineIntoIs the enthalpy of the inlet steam of the turbine, hRow boardFor the exhaust enthalpy of the turbine, NDecrease in the thickness of the steelFor power loss, MDrawerThe amount of extracted steam is hDrawerIs the enthalpy of the extracted steam;
the air extraction amount is calculated according to the formula (10),
m in formula (10)DrawerFor the amount of extracted steam, MFor supplying toFor the required heat supply, hDrawerIs the enthalpy of the extraction, hFor supplying toFor supplying enthalpy of steam or hot water, hReducingIs the enthalpy of the desuperheated water;
the heating requirements of the power station are usuallyThe heat supply is usually required by low-pressure saturated steam or hot water, and the extracted steam is usually superheated steam, so that the temperature is required to be reduced; if the superheated steam supplies heat, calculating the required superheated steam quantity by referring to the calculating method, and correspondingly reducing the steam inlet quantity of the steam turbine; the process in which the steam works in the turbine is an adiabatic expansion process, hRow boardThe temperature of the steam turbine exhaust steam is related to the circulating water temperature of the cooling tower and finally related to the wet bulb temperature, so that the water inlet and outlet temperature and the circulating water quantity of the circulating water can be calculated;
the step also comprises the steps of calculating the motor running power of the waste heat power generation auxiliary machine,
the operating power of the fan is according to the formula
The calculation is carried out according to the calculation,
the running power of the water pump is according to the formula
The calculation is carried out according to the calculation,
q in the formulae (11) and (12)vIs volume flow, p is fan full pressure, ρ is fluid density, H is pump head, ηGeneral assembly、ηtm、ηgThe total efficiency, prime mover efficiency, and transmission efficiency of the pump and fan, respectively; the air quantity of a fan of the cooling tower can be determined by multiplying the circulating water quantity by the steam-water ratio;
d. judging whether the power generation power of the steam turbine is the maximum value, if so, outputting a waste heat boiler result parameter: the method comprises the steps of steam production, steam pressure, narrow point temperature difference (final value) and flue gas waste heat recovery rate;
turbine result parameters: the method comprises the steps of generating power, steam inlet temperature and flow and steam extraction parameters (flow, temperature and pressure);
pipe network result parameters: including pipe diameter (final value), insulation thickness (final value), pressure loss and temperature loss;
and (3) the result parameters of auxiliary equipment of the waste heat power station are as follows: the system comprises motor running power, installed power, self-electricity consumption and self-electricity consumption rate of a waste heat power station, circulating water quantity and water temperature of each pump and fan;
if the steam turbine inlet pressure is not the maximum value, adjusting the steam turbine inlet pressure which is adjusted and set, and repeating the steps a, b and c.
The following three constraint values are checked in the above calculation process:
the narrow-point temperature difference value of the waste heat boiler is not too small, usually 20-30 ℃, and if the value is too small, the heating surface required by the waste heat boiler is obviously increased, so that the waste heat boiler is not economical; if the temperature difference at the narrow point is too small, the steam pressure should be increased.
The temperature difference of the steam at the outlet of the waste heat boiler before and after temperature reduction tends to 0 value; the data may be automatically calculated to the constraint value.
The surplus of the deaerator for deaerating heat should be positive and slightly larger than 0. The data may be automatically calculated to the constraint value.
Varying the steam pressure p of the admission of the steam turbineIntoAnd obtaining a different turbine power generation value. It can be found that under the condition of meeting the constraint conditions, a pressure value exists, the corresponding power generation power value is the maximum, and the utilization rate of the flue gas waste heat is the maximum under the pressure.
The foregoing is merely a preferred embodiment of the invention and is not intended to limit the invention in any manner; those skilled in the art can make numerous possible variations and modifications to the present teachings, or modify equivalent embodiments to equivalent variations, without departing from the scope of the present teachings, using the methods and techniques disclosed above. Therefore, any simple modification, equivalent replacement, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the scope of the protection of the technical solution of the present invention.
Claims (2)
1. A method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation is characterized by comprising the following steps:
a. the steam production of the waste heat boiler is calculated,
a1, firstly, calculating an acid dew point to obtain the exhaust gas temperature of the waste heat boiler; and then calculating the enthalpy value data of each component of the flue gas to obtain enthalpy thermometers of a superheat section, a denitration system empty tube box, an evaporation section, a coal saving section and an oxygen removal evaporation section of the waste heat boiler, wherein the enthalpy value of each section of the flue gas of the waste heat boiler is calculated according to a formula (1):
Qi＝Gi[∑miIi+(ai-1)Ica] (1)
q in formula (1)iIs the total enthalpy value G of the flue gas at a certain temperatureiAs the flue gas flow rate at this temperature, miIs the mole percentage of a certain component, IiTo the enthalpy of the corresponding component at that temperature, IcaIs the enthalpy of air at that temperature, aiThe air leakage rate is relative to the inlet of the waste heat boiler at the temperature;
a2, determining the flue gas temperature of each section of the waste heat boiler as follows:
superheater inlet temperature T1Superheater outlet/evaporator inlet temperature T2Evaporator outlet/economizer inlet temperature T3Temperature T at the exit of economizer/inlet of deaerator4Inlet/exhaust temperature T of oxygen removal evaporator5；
T1The inlet flue gas temperature of the waste heat boiler;
by the formula Q1-Q2＝M·(h1-h2) (2) calculating the smoke at T2The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer2(ii) a Wherein Q1、h1The total enthalpy value of the flue gas, the enthalpy value of the working medium and Q of the inlet of the superheater are respectively2、h2The total enthalpy value of the flue gas at the outlet of the superheater and the enthalpy value of the working medium are respectively, and M is the flow of the working medium, namely the steam production of the waste heat boiler;
T3steam drum saturation temperature + narrow point temperature difference
By the formula Q3-Q4M (1+ blowdown rate) · (h)3-h4) (3) calculating the smoke at T4The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer4(ii) a Wherein Q3、h4Respectively to save coalTotal enthalpy value of flue gas at inlet of device, enthalpy value of working medium, Q2、h2The total enthalpy value of the smoke at the outlet of the economizer and the enthalpy value of the working medium are respectively;
m is calculated according to equation (4):
M＝(Q1-Q3)/(h1-h3) + blowdown rate (h)3’-h3) Wherein h is3' is the saturated hydrothermal enthalpy value of the steam drum; the calculation of M and T2The calculation of (2) is a loop iteration calculation;
judging whether the narrow point temperature difference meets the requirement, and if so, keeping calculation for standby; if not, adjusting the steam inlet pressure of the steam turbine which is adjusted and set, and repeating the step a2 to calculate;
b. calculating the pressure loss and the temperature loss of the feed water and the steam,
b1, calculating the pressure loss delta p of the pipe network according to the formula (5),
in the formula (5)
Is the friction coefficient of the pipeline, L is the length of the pipeline, zeta is the local resistance coefficient, ν is the medium flow rate, g is the gravitational acceleration;
the temperature loss and the heat preservation thickness of the pipe network are calculated according to the formulas (6) and (7),
d in the formulae (6) and (7)0Is the outside diameter of the pipe, D1The outer diameter of the heat-insulating layer is the heat-insulating thickness, gamma is the heat conductivity of the heat-insulating material, KrTo add a heat loss coefficient, cIs the specific heat capacity of the medium, TAAnd TBRespectively, the medium temperature at the starting point and the end point of the pipeline, TaThe temperature is the ambient temperature, and alpha is the surface heat transfer coefficient of the outer surface of the insulating layer to the atmosphere;
judging whether the pressure loss and the temperature loss exceed set values, if so, adjusting the pipe network parameters to repeat the calculation of b1, and if not, performing the step b 2;
b2, calculating the mixed steam temperature of the steam of each waste heat boiler in front of the steam turbine,
first pass through
Calculating to obtain enthalpy value of mixed steam, and determining T according to steam propertyMixing of；
c. Calculating the power generation capacity of the steam turbine,
the generated power N of the steam turbine is calculated according to the formula (9):
N＝ηη1η2[MintohInto-(MInto-MDrawer)-MDrawerhDrawer]/3600 (9)，
Eta, eta in formula (9)1Relative internal efficiency, mechanical efficiency, eta, of the steam turbine, respectively2For generator efficiency, MIntoIs the steam inlet volume, h, of the steam turbineIntoIs the enthalpy of the inlet steam of the turbine, hRow boardFor the exhaust enthalpy of the turbine, NDecrease in the thickness of the steelFor power loss, MDrawerThe amount of extracted steam is hDrawerIs the enthalpy of the extracted steam;
the air extraction amount is calculated according to the formula (10),
m in formula (10)DrawerFor the amount of extracted steam, MFor supplying toFor the required heat supply, hDrawerIs the enthalpy of the extraction, hFor supplying toFor supplying enthalpy of steam or hot water, hReducingIs the enthalpy of the desuperheated water;
d. judging whether the power generation power of the steam turbine is the maximum value, and if so, outputting a waste heat boiler result parameter, a steam turbine result parameter and a pipe network result parameter; if the steam turbine inlet pressure is not the maximum value, adjusting the steam turbine inlet pressure which is adjusted and set, and repeating the steps a, b and c.
2. The method for optimizing the utilization of the residual heat and the generated energy of the glass kiln smoke residual heat power generation as claimed in claim 1, wherein the step c further comprises calculating the motor operating power of the residual heat power generation auxiliary machine,
the operating power of the fan is according to the formula
The calculation is carried out according to the calculation,
the running power of the water pump is according to the formula
The calculation is carried out according to the calculation,
q in the formulae (11) and (12)vIs volume flow, p is fan full pressure, ρ is fluid density, H is pump head, ηGeneral assembly、ηtm、ηgThe total efficiency, prime mover efficiency, and transmission efficiency of the pump and fan, respectively;
and d, outputting the result parameters of the auxiliary equipment of the waste heat power station after judging that the power generation power of the steam turbine is the maximum value.
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