CN112066742B - Method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation - Google Patents
Method for optimizing utilization of waste heat and generated energy of glass kiln flue gas waste heat power generation Download PDFInfo
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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
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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- Y02E40/70—Smart grids as climate change mitigation technology in the energy generation sector
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
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- Y04S10/50—Systems or methods supporting the power network operation or management, involving a certain degree of interaction with the load-side end user applications
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 the steam turbine is not the maximum value, adjusting the set steam inlet pressure of the steam turbine and repeating the steps a, b and c for calculation; 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 problem 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 enthalpy value data of each component of the flue gas to obtain enthalpy thermometers of a superheating section, a denitration system empty pipe box, an evaporation section, a coal saving section and a deoxygenation 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):
Q i ＝G i [∑m i I i +(a i -1)I ca ] (1)
q in formula (1) i Is the total enthalpy value G of the flue gas at a certain temperature i As the flue gas flow rate at this temperature, m i Is the mole percentage of a certain component,I i to the enthalpy of the corresponding component at that temperature, I ca Is the enthalpy of air at that temperature, a i The 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 T 1 Superheater outlet/evaporator inlet temperature T 2 Evaporator outlet/economizer inlet temperature T 3 Temperature T at the exit of economizer/inlet of deaerator 4 Outlet/flue gas temperature T of deaerating evaporator 5 ；
T 1 The inlet flue gas temperature of the waste heat boiler;
by the formula Q 1 -Q 2 ＝M·(h 1 -h 2 ) (2) calculating the smoke at T 2 The enthalpy value of the flue gas is reversely solved to obtain T through a flue gas enthalpy thermometer 2 (ii) a Wherein Q 1 、h 1 Respectively the total enthalpy value of the flue gas at the inlet of the superheater, the enthalpy value of the working medium, Q 2 、h 2 The 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 rate of the working medium, namely the steam production capacity of the waste heat boiler;
T 3 steam drum saturation temperature plus narrow point temperature difference
By the formula Q 3 -Q 4 M (1+ pollution discharge rate) · (h) 3 -h 4 ) (3) calculating to obtain the smoke at T 4 The enthalpy value of the time and the heat is reversely solved to obtain T through a smoke enthalpy thermometer 4 (ii) a Wherein Q 3 、h 3 The total enthalpy value of the smoke gas, the enthalpy value of the working medium and Q of the inlet of the coal economizer respectively 4 、h 4 The 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＝(Q 1 -Q 3 )/(h 1 -h 3 ) + blowdown rate (h) 3 ’-h 3 ) Wherein h is 3 ' is the saturated hydrothermal enthalpy value of the steam drum; the sum T of the M 2 The 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 set steam turbine inlet pressure and repeating the calculation of the step a 2;
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)
The coefficient of friction of the pipeline is shown, L is the length of the pipeline, zeta is the local resistance coefficient, ν is the medium flow rate, and g is the gravity 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) 0 Is the outside diameter of the pipe, D 1 The outer diameter of the heat preservation layer, delta is the heat preservation thickness, lambda is the heat conductivity of the heat preservation material, K r C is the specific heat capacity of the medium, T A And T B Respectively, the medium temperature at the starting point and the end point of the pipeline, T a The 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 the enthalpy value of the mixed steam, and solving the T mixing through the property of the steam;
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＝ηη 1 η 2 [M go into h Into -(M Go into -M Drawer )h Row board -M Drawing-out device h Drawing-out device -N Damage to ]/3600 (9)，
In the formula (9), eta and eta 1 are the relative internal efficiency and mechanical efficiency of the steam turbine respectively, eta 2 is the efficiency of the generator, M Go into For the steam admission, h, of the steam turbine Go into Is the enthalpy of the inlet steam of the turbine, h Row board Is the exhaust enthalpy value of the steam turbine, N Decrease in the thickness of the steel For power loss, M Drawing-out device Is the steam extraction h of the steam turbine Drawing-out device Is the enthalpy of the extracted steam;
the air extraction amount is calculated according to a formula (10),
m in the formula (10) Drawing-out device For the extraction of steam, M For supplying to For the required heat supply, h Drawing-out device Is the enthalpy of the extraction, h Into For supplying enthalpy of steam or hot water, h Reducing the weight of Is 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 set steam turbine inlet pressure, 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 in such a way that,
the running power of the water pump is according to the formula
The calculation is carried out in such a way that,
q in the formulae (11) and (12) v Is the volume flow, p is the fan full pressure, ρ is the fluid density, H is the pump head, η General assembly 、η tm 、η g The total efficiency of the pump and the fan, the prime mover efficiency and the transmission efficiency are 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 furnace, provide power outwards and provide steam or hot water required by production and living, 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, so that the unconditional adaptation is required for the flue gas parameters discharged by the glass melting furnace, and the 'quantity of the flue gas and the quantity of the consumed gas' are realized.
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 figure 1, the invention provides a method for optimizing utilization of waste heat and generated energy of glass kiln smoke 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 of the flue gas and the steam yield 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 thermometers of a waste heat boiler superheating section, a denitration system empty pipe 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 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 set steam turbine inlet pressure, and repeating the steps a, b and c.
And (c) during the calculation of the steps a, b and c, constructing constraint conditions according to the acid dew point temperature of the flue gas, the narrow point temperature difference of the waste heat boiler and the temperature difference of steam at the outlet of the waste heat boiler before and after temperature reduction.
The mode for calculating the maximization of the generating power of the steam turbine is as follows:
and (3) giving an initial value of the steam pressure at the inlet of the steam turbine, 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):
Q i ＝G i [∑m i I i +(a i -1)I ca ] (1)
q in formula (1) i Is the total enthalpy value G of the flue gas at a certain temperature i As the flue gas flow rate at this temperature, m i Is the mole percentage of a certain component, I i To the enthalpy of the corresponding component at that temperature, I ca Is the enthalpy of air at that temperature, a i The 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 T 1 Superheater outlet/evaporator inlet temperature T 2 Evaporator outlet/economizer inlet temperature T 3 Temperature T at the exit of economizer/inlet of deaerator 4 Outlet/flue gas temperature T of deaerating evaporator 5 ；
T 1 The inlet flue gas temperature of the waste heat boiler;
by the formula Q 1 -Q 2 ＝M·(h 1 -h 2 ) (2) calculating the enthalpy value of the flue gas at T2, and solving T reversely through a flue gas enthalpy thermometer 2 (ii) a Wherein Q 1 、h 1 The total enthalpy value of the flue gas, the enthalpy value of the working medium and Q of the inlet of the superheater are respectively 2 、h 2 The 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;
T 3 steam drum saturation temperature + narrow point temperature difference
By the formula Q 3 -Q 4 M (1+ blowdown rate) · (h) 3 -h 4 ) (3) calculating the enthalpy value of the flue gas at T4, and solving T reversely through a flue gas enthalpy thermometer 4 (ii) a Wherein Q 3 、h 3 The total enthalpy value of the smoke gas, the enthalpy value of the working medium and Q of the inlet of the coal economizer respectively 4 、h 4 The total enthalpy value of the flue gas at the outlet of the coal economizer and the enthalpy value of the working medium are respectively;
m is calculated according to equation (4):
M＝(Q 1 -Q 3 )/(h 1 -h 3 ) + blowdown rate (h) 3 ’-h 3 ) Wherein h is 3 ' is the saturated water enthalpy value of the steam drum; the calculation of M and T 2 The 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 set steam turbine inlet pressure and repeating the calculation of the step a 2;
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 pipe friction coefficient, L is the pipe length, zeta is the local resistance coefficient, v is the medium flow rate, g isAcceleration of gravity;
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) 0 Is the outside diameter of the pipe, D 1 The outer diameter of the heat preservation layer, delta is the heat preservation thickness, lambda is the heat conductivity of the heat preservation material, K r Adding heat loss coefficient, c is specific heat capacity of medium, T A And T B Respectively, the starting and end point medium temperatures, T, of the pipeline a The 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:
p 1 -Δp 1 ＝p 2 -Δp 2 ＝p i -Δp i ＝p into + Δ p', where p Into + 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 property Mixing 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＝ηη 1 η 2 [M into h Into -(M Into -M Drawer )h Row board -M Drawer h Drawing-out device -N Damage to ]/3600 (9)
Eta, eta in formula (9) 1 Relative internal efficiency, mechanical efficiency, eta, of the steam turbine, respectively 2 For generator efficiency, M Into Is the steam inlet volume, h, of the steam turbine Into Is the enthalpy of the inlet steam of the turbine, h Row board For the exhaust enthalpy of the turbine, N Decrease in the thickness of the steel For power loss, M Drawer Is the steam extraction h of the steam turbine Drawer Is the enthalpy of the extracted steam;
the air extraction amount is calculated according to the formula (10),
m in the formula (10) Drawer For the amount of extracted steam, M For supplying to For the required heat supply, h Drawing-out device Is the enthalpy of the extraction, h Into For supplying enthalpy of steam or hot water, h Reducing the weight of Is the enthalpy of the desuperheated water;
the heating demand of the power station is usually provided by steam extraction of a steam turbine, the heating usually needs low-pressure saturated steam or hot water, the steam extraction usually is superheated steam, and therefore temperature reduction is needed; 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, h Row board The temperature of the steam turbine exhaust 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 calculating the motor running power of the waste heat power generation auxiliary machine,
the running power of the fan is according to the formula
The calculation is carried out in such a way that,
the running power of the water pump is according to the formula
The calculation is carried out in such a way that,
qv in the formulas (11) and (12) is volume flow, p is full pressure of the fan, rho is fluid density, H is pump head, eta is General assembly 、η tm 、η g The 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 set steam turbine inlet pressure, and repeating the steps a, b and c.
The following three constraint values are checked in the above calculation process:
the temperature difference value of the narrow point 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 deaerating heat of the deaerator is a positive value and is slightly larger than a 0 value. The data may be automatically calculated to the constraint value.
Varying the steam pressure p of the admission of the turbine Into And 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 illustrative of the preferred embodiments of the present invention, and is not to be construed as limiting thereof in any way; those skilled in the art can make many possible variations and modifications to the disclosed solution, or to modify equivalent embodiments, without departing from the scope of the solution, using the methods and techniques disclosed above. Therefore, any simple modifications, equivalent substitutions, equivalent changes and modifications made to the above embodiments according to the technical essence of the present invention are within the scope of the technical scheme 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):
Q i ＝G i [∑m i I i +(a i -1)I ca ] (1)
q in formula (1) i Is the total enthalpy value G of the flue gas at a certain temperature i As the flue gas flow rate at this temperature, m i Is the mole percentage of a certain component, I i To the enthalpy of the corresponding component at that temperature, I ca Is the enthalpy of air at that temperature, a i Is a leakage of the inlet of the waste heat boiler at the temperatureThe wind rate;
a2, determining the flue gas temperature of each section of the waste heat boiler as follows:
superheater inlet temperature/waste heat boiler inlet flue gas temperature T 1 Superheater outlet/evaporator inlet temperature T 2 Evaporator outlet/economizer inlet temperature T 3 Temperature T at the exit of economizer/inlet of deaerator 4 Outlet/flue gas temperature T of deaerating evaporator 5 ；
T 1 The inlet flue gas temperature of the waste heat boiler;
by Q 1 -Q 2 ＝M·(h 1 -h 2 ) (2) calculating the temperature T of the flue gas at the outlet of the superheater and the inlet of the evaporator 2 The enthalpy value is reversely solved through a smoke enthalpy thermometer to obtain the superheater outlet/evaporator inlet temperature T 2 (ii) a Wherein Q 1 、h 1 Respectively the total enthalpy value of the flue gas at the inlet of the superheater, the enthalpy value of the working medium, Q 2 、h 2 The 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;
evaporator outlet/economizer inlet temperature T 3 Steam drum saturation temperature + narrow point temperature difference
By the formula Q 3 -Q 4 M (1+ pollution discharge rate) · (h) 3 -h 4 ) (3) calculating the temperature T of the flue gas at the outlet of the economizer/the inlet of the oxygen removal evaporator 4 The enthalpy value of the coal economizer/the inlet temperature T of the oxygen removal evaporator is solved reversely through a smoke enthalpy thermometer 4 (ii) a Wherein Q 3 、h 3 The total enthalpy value of the smoke gas, the enthalpy value of the working medium and Q of the inlet of the coal economizer respectively 4 、h 4 The total enthalpy value of the flue gas at the outlet of the coal economizer and the enthalpy value of the working medium are respectively;
the working medium flow M is calculated according to the formula (4):
M＝(Q 1 -Q 3 )/(h 1 -h 3 ) + blowdown rate (h3 '-h 3), wherein h 3' is the saturated hydrothermal enthalpy value of the steam drum; calculating the flow M of the working medium and the inlet temperature T of the superheater outlet/evaporator 2 The 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 set steam turbine inlet pressure and repeating the calculation of the step a 2;
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 pipe friction coefficient, L is the pipe length, zeta is the local resistance coefficient, v is the medium flow rate, g is the gravitational acceleration, D 0 Is the outer diameter of the pipeline;
the temperature loss and the heat preservation thickness of the pipe network are calculated according to the formulas (6) and (7),
d in the formulas (6) and (7) 0 Is the outside diameter of the pipe, D 1 The outer diameter of the heat preservation layer, delta is the heat preservation thickness, lambda is the heat conductivity of the heat preservation material, K r C is the specific heat capacity of the medium, T A And T B Respectively, the starting and end point medium temperatures, T, of the pipeline a The 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 the enthalpy value h of the mixed steam of each waste heat boiler Mixing of Then the steam temperature T of the mixed steam of the waste heat boilers is obtained through the steam property Mixing 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＝ηη 1 η 2 [M into h Go into -(M Go into -M Drawing-out device )h Row board -M Drawing-out device h Drawing-out device -N Damage to ]/3600 (9)
Eta, eta in formula (9) 1 Relative internal efficiency, mechanical efficiency, eta, of the steam turbine, respectively 2 For generator efficiency, M Into Is the steam inlet volume, h, of the steam turbine Go into Is the enthalpy of the steam turbine inlet, h Row board Is the exhaust enthalpy value of the steam turbine, N Decrease in the thickness of the steel For power loss, M Drawer Is the steam extraction h of the steam turbine Drawer Is the enthalpy of the extracted steam;
the air extraction amount is calculated according to the formula (10),
m in the formula (10) Drawing-out device For the extraction of steam, M For supplying to For the required heat supply, h Drawing-out device Is the enthalpy of the extraction, h Go into For supplying enthalpy of steam or hot water, h Reducing the weight of Is 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 set steam turbine inlet pressure, 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 running power of the fan is according to the formula
The calculation is carried out in such a way that,
the running power of the water pump is according to the formula
The calculation is carried out in such a way that,
q in the formulae (11) and (12) v Is the volume flow, p is the fan full pressure, ρ is the fluid density, H is the pump head, η General (1) 、η tm 、η g The 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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| CN201819201U (en) * | 2010-10-13 | 2011-05-04 | 广东开能环保能源有限公司 | Glass furnace pure low-temperature waste heat generating system |
| CN103727514A (en) * | 2013-12-14 | 2014-04-16 | 蚌埠玻璃工业设计研究院 | Exhaust gas temperature adjusting device of waste heat power generation boiler of glass kiln |
| CN108019733A (en) * | 2016-11-23 | 2018-05-11 | 林振娴 | A kind of computational methods for determining three discard heat boiler steam flows and parameter of discharging fume |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201819201U (en) * | 2010-10-13 | 2011-05-04 | 广东开能环保能源有限公司 | Glass furnace pure low-temperature waste heat generating system |
| CN103727514A (en) * | 2013-12-14 | 2014-04-16 | 蚌埠玻璃工业设计研究院 | Exhaust gas temperature adjusting device of waste heat power generation boiler of glass kiln |
| CN108019733A (en) * | 2016-11-23 | 2018-05-11 | 林振娴 | A kind of computational methods for determining three discard heat boiler steam flows and parameter of discharging fume |
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Address after: 518054 5 / F, east block, beiyihai Plaza, Chuangye Road, Nanshan District, Shenzhen City, Guangdong Province Patentee after: Shenzhen Kaisheng Technology Engineering Co.,Ltd. Patentee after: China Building Materials Glass New Materials Research Institute Group Co.,Ltd. Patentee after: China Triumph International Engineering Co.,Ltd. Address before: 518054 5 / F, east block, beiyihai Plaza, Chuangye Road, Nanshan District, Shenzhen City, Guangdong Province Patentee before: SHENZHEN TRIUMPH TECHNOLOGY ENGINEERING Co.,Ltd. Patentee before: China Building Materials Glass New Materials Research Institute Group Co.,Ltd. Patentee before: China Triumph International Engineering Co.,Ltd. |