CN114154103A - Method for calculating energy-saving effect of deep utilization system of flue gas waste heat of coal-fired boiler - Google Patents
Method for calculating energy-saving effect of deep utilization system of flue gas waste heat of coal-fired boiler Download PDFInfo
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Abstract
The invention discloses a method for calculating the energy-saving effect of a deep flue gas waste heat utilization system of a coal-fired boiler, in particular relates to a method for correcting and calculating the energy-saving effect of a tail flue of the coal-fired boiler after the deep flue gas waste heat utilization system is additionally arranged, and belongs to the field of coal-fired power generation. The deep utilization system of the flue gas waste heat comprises two stages of low-pressure economizers, wherein the first stage of low-pressure economizer heats condensed water, the second stage of low-pressure economizer heats the condensed water or closed circulating water, and the condensed water or the closed circulating water is used for heating boiler inlet air. The method calculates the difference value of the unit power supply coal consumption rates under two working conditions of the operation and shutdown flue gas waste heat deep utilization system as the energy-saving effect of the flue gas waste heat deep utilization system, and compared with the traditional energy-saving effect analysis and calculation method, the method is relatively simple and has few influence factors.
Description
Technical Field
The invention relates to a method for calculating the energy-saving effect of a deep flue gas waste heat utilization system of a coal-fired boiler, in particular to a method for correcting and calculating the energy-saving effect of a tail flue of the coal-fired boiler after the deep flue gas waste heat utilization system is additionally arranged, and belongs to the field of coal-fired power generation.
Background
In order to improve the economy of a power plant, a coal-fired power generating set generally adopts a flue gas waste heat utilization technology. At present, the development of the flue gas waste heat utilization technology on a coal-fired unit mainly has the following forms: the traditional low-pressure economizer form, a flue gas waste heat deep utilization system and a flue gas waste heat high-energy level waste heat utilization technology (a machine-furnace deep coupling technology). The energy-saving effect of the traditional low-pressure economizer is analyzed and calculated according to specific application cases, and DL/T1885 'Low-pressure economizer performance test guide' provides a method for testing the performance of the traditional low-pressure economizer and calculating the energy-saving effect. The flue gas waste heat deep utilization system comprises two stages of low-pressure economizers, the first stage of low-pressure economizer heats condensed water, the steam extraction of a turbine regenerative system is reduced, and the heat consumption rate of a turbine is reduced; the secondary low-pressure economizer heats condensed water or closed circulating water, the condensed water or the closed circulating water is used for heating boiler inlet air, and when the condensed water absorbs or releases heat from flue gas to the flue gas, the inlet air temperature of the boiler changes, so that the efficiency of the boiler is influenced.
Because the traditional low-pressure economizer does not influence the calculation of the boiler efficiency, the energy-saving effect analysis and calculation method does not usually relate to the boiler, but the flue gas waste heat deep utilization system heats the inlet air of the boiler through the secondary low-pressure economizer, so that the calculation of the boiler efficiency is influenced. According to the traditional energy-saving effect analysis and calculation method, a steam turbine and boiler performance test and a plant power rate test are generally carried out under two working conditions of a flue gas waste heat utilization system in operation and shutdown, and the difference value of the unit power supply coal consumption rate under the two working conditions is calculated to serve as the energy-saving effect of the flue gas waste heat deep utilization system. However, comprehensive and accurate steam turbine and boiler tests are troublesome, the workload is high, meanwhile, the energy-saving effect of the flue gas waste heat deep utilization system is greatly influenced by operation parameters and a unit thermodynamic system, the influence factors are numerous, the test result reproducibility is poor, and the accurate evaluation of the energy-saving effect is greatly influenced.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provides a method for calculating the energy-saving effect of a coal-fired boiler flue gas waste heat deep utilization system.
The technical scheme adopted by the invention for solving the problems is as follows: a method for calculating the energy-saving effect of a deep utilization system of flue gas waste heat of a coal-fired boiler is characterized by comprising the following steps of:
the method comprises the following steps: carrying out thermal performance tests of a steam turbine and a boiler under the condition of the shutdown flue gas waste heat deep utilization system, and calculating the test heat consumption rate of the steam turbine set, the corrected heat consumption rate, the test thermal efficiency of the boiler and the corrected thermal efficiency; synchronously measuring the plant power consumption rate of the unit, and measuring the power consumption of a condensate pump of a steam turbine, a booster pump of a flue gas waste heat deep utilization system and a draught fan of a boiler;
step two: under the conditions of the same electric load working condition and the consistency of the host machine operation parameters and the operation mode, performing a thermal performance test of the steam turbine under the working condition of the operating flue gas waste heat deep utilization system, and calculating the test heat consumption rate of the steam turbine and the corrected heat consumption rate; the inlet air temperature of a boiler at the inlet and the outlet of a secondary low-pressure economizer in the flue gas waste heat deep utilization system is synchronously measured, and the power consumption of a steam turbine condensate pump, a flue gas waste heat deep utilization system booster pump and a boiler induced draft fan is measured;
step three: calculating the power consumption change values of a condensate pump, a booster pump and a boiler induced draft fan, and calculating the plant power consumption rate of the unit under the operation condition of the flue gas waste heat deep utilization system;
step four: calculating the power supply coal consumption rate of the unit under the condition by utilizing the heat consumption rate of the steam turbine, the boiler efficiency and the plant power consumption rate of the unit under the shutdown condition of the flue gas waste heat deep utilization system;
step five: correcting the boiler efficiency under the operation stop condition by utilizing the inlet air temperature of the boiler under the operation condition of the flue gas waste heat deep utilization system to obtain the boiler efficiency under the operation condition;
step six: calculating the power supply coal consumption rate of the unit under the working condition by utilizing the heat consumption rate of the steam turbine, the plant power consumption rate of the unit and the boiler efficiency under the working condition of the flue gas waste heat deep utilization system;
step seven: and calculating the reduction value of the unit power supply coal consumption rate under the operation condition of the flue gas waste heat deep utilization system, and taking the reduction value as the energy-saving effect of the flue gas waste heat deep utilization system.
The specific steps of the first step are as follows:
(1) calculating unit test heat consumption rate H under shutdown working condition of flue gas waste heat deep utilization systemt0The calculation formula is (for the single reheating unit):
Ht0=[Fms0×(hms0-hfw0)+Fcrh0×(hhrh0-hcrh0)+Fgr0×(hms0-hgr0)+Fzr0×(hhrs0-hzr0)]/Pe0
wherein: ht0To test the heat rate, hms0Is the main steam enthalpy, hfw0For the final feed water enthalpy, hhrh0Is the reheat steam enthalpy, hcrh0For the exhaust enthalpy, h, of the high-pressure cylindergr0For reducing the enthalpy of water, h, of the superheaterzr0Reducing the enthalpy of water for reheaters, Fms0Main steam flow, Fcrh0Is the exhaust flow of the high-pressure cylinder, Fgr0For reducing the temperature and water flow of superheater Fzr0For reducing the temperature water flow, P, of the reheatere0Is the power of the generator;
the flow is calculated by the thermodynamic performance test data of the steam turbine, and the enthalpy values of the steam and the water are obtained by measuring the pressure and the temperature of corresponding parts and looking up an enthalpy entropy table;
(2) calculating the corrected heat consumption rate H of the unit under the shutdown condition of the flue gas waste heat deep utilization systemr0The calculation formula is (for the single reheating unit):
Hr0=Ht0/(C10×C20×C30×C40×C50×C60×C70)
wherein Hr0To correct for heat rate, C10、C20、C30、C40、C50、C60、C70The correction coefficients of main steam pressure, main steam temperature, reheat steam loss rate, reheat steam temperature, low-pressure cylinder exhaust steam pressure, superheater desuperheating water flow and reheater desuperheating water flow to heat consumption rate are obtained by checking a correction curve provided by a manufacturing plant; if the superheater attemperation water flow and the reheater attemperation water flow are 0, C in the above formula60=0、C70=0；
(3) Calculating boiler efficiency eta under shutdown working condition of flue gas waste heat deep utilization systemg0The calculation formula is as follows:
ηg0= 100-（q2+q3+q4+q5+q6+qoth-qex）
wherein: etag0For the thermal efficiency of the boiler, q2For heat loss of exhaust gas, q3Heat loss due to incomplete combustion of gas, q4Heat loss due to incomplete combustion of solids, q5For heat loss of boiler, q6Is the physical heat loss of ash, qothFor other heat losses, qexThe data are the percentage of the external heat and the lower heating value of the fuel and are obtained by a boiler performance test.
The second step comprises the following specific steps:
(1) calculating unit test heat consumption rate H under operation condition of flue gas waste heat deep utilization systemt1The calculation formula is (for the single reheating unit):
Ht1=[Fms1×(hms1-hfw1)+Fcrh1×(hhrh1-hcrh1)+Fgr1×(hms1-hgr1)+Fzr1×(hhrs1-hzr1)]/Pe1
wherein: ht1To test the heat rate, hms1Is the main steam enthalpy, hfw1For the final feed water enthalpy, hhrh1Is the reheat steam enthalpy, hcrh1For the exhaust enthalpy, h, of the high-pressure cylindergr1Reducing water enthalpy for superheater，hzr1Reducing the enthalpy of water for reheaters, Fms1Main steam flow, Fcrh1Is the exhaust flow of the high-pressure cylinder, Fgr1For reducing the temperature and water flow of superheater Fzr1For reducing the temperature and water flow rate, P, of the superheatere1Is the power of the generator;
the flow is calculated by the thermal performance test data of the steam turbine under the operation condition of the flue gas waste heat utilization system, the enthalpy values of the steam and the water are obtained by measuring the pressure and the temperature of the corresponding parts and looking up an enthalpy entropy table, and P is kept as much as possible in the test processe1And Pe0The same;
(2) calculating the corrected heat rate H of the unit under the operation condition of the flue gas waste heat deep utilization systemr1The calculation formula is (for the single reheating unit):
Hr1=Ht1/(C11×C21×C31×C41×C51×C61×C71)
wherein Hr1To correct for heat rate, C11、C21、C31、C41、C51、C61、C71The correction coefficients of main steam pressure, main steam temperature, reheat steam loss rate, reheat steam temperature, low-pressure cylinder exhaust steam pressure, superheater desuperheating water flow and reheater desuperheating water flow to heat consumption rate are obtained by checking a correction curve provided by a manufacturing plant; if the superheater attemperation water flow and the reheater attemperation water flow are 0, C in the above formula61=0、C71=0。
The third step comprises the following specific steps:
(1) calculating the service power rate L under the shutdown condition of the flue gas waste heat deep utilization systemcy0The calculation formula is as follows:
Lcy0 = Pcy0×100/Pe0
wherein L iscy0The plant power rate; pcy0The measured value is the plant power consumption; pe0Testing the measured value for the power of the generator;
(2) calculating the service power rate L under the operation condition of the flue gas waste heat deep utilization systemcy1The calculation formula is：
Lcy1 =（Pcy0+ΔPzyb+ΔPnb+ΔPyfj）×100 / Pe1
Wherein L iscy1The plant power rate; delta PzybIncrease the power consumption of the booster pump by delta PnbFor increasing the power consumption of the coagulation pump, Δ PyfjThe data are obtained by actual measurement in the test for increasing the power consumption of the induced draft fan.
The fourth step comprises the following specific steps:
calculating the unit power supply coal consumption rate b under the shutdown condition of the flue gas waste heat deep utilization system by using the corrected steam turbine heat consumption rate, the boiler efficiency and the unit plant power consumption rate obtained in the first step, the second step and the third stepg0The calculation formula is as follows:
bg0 = Hr0×105/[ηg0×ηgd×7000×4.1868×(1-Lcy0/100)]
wherein eta isgdFor pipeline efficiency, a design value of 0.99 was taken.
The concrete steps of the fifth step are as follows:
correcting the exhaust smoke temperature by using the air inlet temperature of the boiler at the outlet (inlet of an air preheater) of the secondary low-pressure economizer under the operation condition of the deep utilization system of the waste heat of the exhaust smoke, and calculating the heat loss of the exhaust smoke by using the exhaust smoke temperature to calculate the corrected boiler efficiency; the correction calculation formula of the exhaust gas temperature is as follows:
θb py=[tb 0×(θ′ ky-θpy)+θ′ ky×(θpy–t0)]/(θ′ ky-t0)
wherein: thetab pyFor conversion to the exhaust gas temperature t at the designed inlet air temperature of the air preheaterb 0For designed air preheater inlet air temperature theta′ kyFor actually measuring the inlet flue gas temperature theta of the air preheaterpyFor actually measuring the outlet flue gas temperature t of the air preheater0Actually measuring the air temperature at the inlet of the air preheater;
designed inlet air temperature tb 0And after conversionExhaust gas temperature thetab pyAnd boiler input heat respectively replaces t in the calculation formula of the heat loss of the exhaust smoke in GB 10184-20150And thetapyThe corrected heat loss q of the exhaust gas can be obtained2And (4) substituting the formula in the step (3) to calculate and obtain the corrected boiler thermal efficiency.
The sixth step comprises the following specific steps:
calculating the unit power supply coal consumption rate b when the flue gas waste heat deep utilization system is put into operation by using the corrected heat consumption rate, the corrected boiler efficiency and the unit plant power consumption rate of the steam turbine under the operating condition of the flue gas waste heat deep utilization system obtained in the second step, the third step and the fifth stepg1The calculation formula is as follows:
bg1 = Hr1×105/[ηg1×ηgd×7000×4.1868×(1-Lcy1/100)]
the concrete steps of the seventh step are as follows:
energy-saving effect of flue gas waste heat deep utilization system is with reduction value delta b of unit power supply coal consumption rate after commissioninggExpressed, the calculation formula is:
Δbg =bg0 - bg1
compared with the prior art, the invention has the following advantages and effects:
(1) for the coal-fired unit provided with the flue gas waste heat deep utilization system, the energy-saving effect of the coal-fired unit is calculated by utilizing the difference value of the power supply coal consumption rates of the unit under two working conditions of the flue gas waste heat deep utilization system in operation and shutdown, the method is simple, and the result is visual.
(2) The flue gas waste heat deep utilization system only has the influence on the boiler efficiency by heating the boiler inlet air by the secondary low-pressure economizer, only carries out the boiler efficiency test under the shutdown working condition during the test, corrects the boiler inlet air temperature to the design value under the commissioning state, and does not need to carry out the boiler efficiency test under the commissioning working condition.
(3) The change of the inlet air temperature is utilized to correct the boiler efficiency, the influence of other operation parameters and system factors on the boiler efficiency caused by the switching problem under the operating and shutdown working conditions of the flue gas waste heat deep utilization system is avoided, and the system error of the boiler test is eliminated.
(4) The influence factors of the plant power rate of the unit are numerous, and only the plant power rate of the outage working condition is measured when the plant power rate of the operation and outage flue gas waste heat deep utilization system is measured. For the operation working condition, the change values of the power consumption of the condensate pump, the flue gas waste heat deep utilization system booster pump and the boiler induced draft fan obtained through measurement are calculated, the method is simple, and the influence of the operation mode and the operation state change of the unit auxiliary machine is avoided.
Drawings
FIG. 1 is a schematic diagram of a gas-water system of a primary low-pressure economizer in an embodiment of the invention.
FIG. 2 is a schematic diagram of a gas-water system of a two-stage low-pressure economizer in the embodiment of the invention.
Detailed Description
The present invention will be described in further detail below by way of examples with reference to the accompanying drawings, which are illustrative of the present invention and are not to be construed as limiting the present invention.
Examples are given.
The embodiment provides a method for calculating the energy-saving effect of a flue gas waste heat deep utilization system of a coal-fired boiler of a subcritical 300 MW-grade unit, which comprises the following steps:
a300 MW grade unit is provided with a smoke waste heat deep utilization system, a boiler is an SG-1025/17.44-M844 subcritical pressure intermediate single reheating control circulation drum furnace produced by a Shanghai boiler plant, and a steam turbine is a C320-16.7/0.8/538/538 type subcritical single intermediate reheating, double-cylinder double-steam-exhaust, single-shaft and steam extraction condensing steam turbine. The deep utilization system of the flue gas waste heat realizes the cascade utilization of the boiler exhaust gas waste heat by adopting a segmented heat exchange technology, and the whole system consists of a primary low-pressure economizer, a secondary low-pressure economizer and a cold end protection device. The primary low-pressure economizer is arranged in a horizontal flue behind the air preheater, the secondary low-pressure economizer is arranged in an inlet flue of the desulfurizing tower, and the cold end protection device is arranged in an outlet air duct of the primary fan and the secondary fan. The schematic diagrams of the gas-water system of the primary low-pressure economizer, the secondary low-pressure economizer and the cold end protection device are shown in fig. 1 and fig. 2.
The primary low-pressure economizer and the main condensation water system are arranged in parallel, the inlet pipeline is designed with a booster pump, and condensation water from the No. 8 low-pressure inlet and the No. 7 low-pressure outlet is mixed and then enters the primary low-pressure economizer to absorb the waste heat of flue gas at the high-temperature section, and then returns to the condensation water pipeline at the No. 5 low-pressure inlet to be merged with the main condensation water. The smoke temperature at the outlet of the primary low-pressure economizer realizes automatic frequency conversion regulation by means of a booster pump. The second-stage low-pressure economizer is arranged behind the second section of the high-temperature heat exchanger of the first-stage low-pressure economizer and is arranged in parallel with the main condensation water system, and a booster pump is designed on an inlet pipeline. The condensate water from No. 8 low inlet and No. 7 low outlet absorbs the flue gas waste heat at the second-level low-pressure economizer after mixing, and partly gets into cold junction protection device heating boiler air supply, then the return water adds the import to No. 8 low, and partly directly gets back to No. 8 low inlet through cold section protection device bypass door, and cold junction protection device arranges in air heater front fan outlet side for the heating gets into one, overgrate air of boiler.
In order to determine the energy-saving effect of the deep utilization system of the flue gas waste heat, the thermal performance tests of the boiler and the steam turbine set are carried out.
The test is carried out under two working conditions of commissioning and decommissioning of the flue gas waste heat deep utilization system, and the energy-saving benefit of the unit flue gas waste heat utilization system after commissioning is calculated by accurately measuring the heat consumption rate of the steam turbine, the boiler efficiency and the change of the plant power consumption rate. In a comparison test of the flue gas waste heat deep utilization system during operation and shutdown under the same load, the main and reheat steam parameters of the two tests are kept consistent as much as possible, the operation modes of other machine and furnace thermodynamic systems except the flue gas waste heat deep utilization system are kept consistent, the operation conditions of main auxiliary equipment are kept consistent before and after, and the inlet condensation water temperature and the exhaust gas temperature of the flue gas waste heat utilization system are used as test boundary conditions.
In the whole test process, the running states of the main engine and the auxiliary engine are good, the thermal system is ensured not to have large leakage through carefully checking all valves which are likely to leak at the boiler side and the steam turbine side, and the operation that the isolation state of the system is likely to change due to soot blowing, fixed continuous discharge and the like is not carried out.
The calculation results of the comparative test under the 320MW working condition of the unit are shown in the tables 1, 2, 3 and 4.
TABLE 1 steam turbine Performance test results calculation Table
| Parameter name | Unit of | 320 MW-outage waste heat utilization system | 320 MW-commissioning waste heat utilization system |
| Power of generator | MW | 319.88 | 320.43 |
| Main steam pressure | MPa | 16.534 | 16.647 |
| Temperature of main steam | ℃ | 532.8 | 533.3 |
| High discharge pressure | MPa | 3.580 | 3.538 |
| High exhaust temperature | ℃ | 322.2 | 321.3 |
| Inlet pressure of intermediate pressure cylinder | MPa | 3.277 | 3.238 |
| Inlet temperature of intermediate pressure cylinder | ℃ | 537.6 | 539.6 |
| Exhaust pressure of intermediate pressure cylinder | MPa | 0.768 | 0.749 |
| Exhaust temperature of intermediate pressure cylinder | ℃ | 329.6 | 329.5 |
| Inlet pressure of low pressure cylinder | MPa | 0.753 | 0.734 |
| Inlet temperature of low pressure cylinder | ℃ | 328.6 | 328.4 |
| Exhaust pressure of low pressure cylinder | kPa | 4.51 | 4.23 |
| Calculating water supply flow | t/h | 976.3 | 958.2 |
| Main steam flow | t/h | 1003.5 | 991.2 |
| Heat absorption of main steam | MJ/h | 2186159.8 | 2162787.7 |
| Heat absorption capacity of reheat steam | MJ/h | 414000.1 | 414289.8 |
| Total heat absorption | MJ/h | 2600159.9 | 2577077.4 |
| Test Heat Rate | kJ/(kW·h) | 8128.53 | 8042.54 |
| Parameter corrected generator power | MW | 323.83 | 321.25 |
| Heat rate after parameter correction | kJ/(kW·h) | 8127.92 | 8061.57 |
| Corrected main steam flow | t/h | 1009.17 | 989.94 |
Table 2 flue gas waste heat deep utilization system test result calculation table
| Parameter name | Unit of | 320 MW-outage waste heat utilization system | 320 MW-commissioning waste heat utilization system |
| High-energy-level heat exchange system | / | ||
| Flow of condensed water inlet side main pipe | t/h | / | 610.2 |
| Condensed water inlet side mother pipe pressure | MPa | / | 1.50 |
| Temperature of condensate water inlet side main pipe | ℃ | / | 61.8 |
| Specific enthalpy of main pipe at water inlet side of condensed water | kJ/kg | / | 259.8 |
| Condensate return side mother pipe pressure | MPa | / | 1.30 |
| Temperature of condensate return side mother pipe | ℃ | / | 88.8 |
| Specific enthalpy of mother pipe at return side of condensed water | kJ/kg | / | 372.8 |
| Condensed water flow of No. 8 low inlet to high temperature heat exchange system | t/h | / | 293.2 |
| Condensate flow rate from No. 7 low heating outlet to high-temperature heat exchange system | t/h | / | 317.0 |
| Condensed water absorbs heat in high-energy-level heat exchange system | MW | / | 19.2 |
| Low-energy-level heat exchange system | |||
| Flow of condensed water inlet side main pipe | t/h | 69.8 | 340.1 |
| Condensed water inlet side mother pipe pressure | MPa | 1.54 | 1.69 |
| Temperature of condensate water inlet side main pipe | ℃ | 50.5 | 62.9 |
| Specific enthalpy of main pipe at water inlet side of condensed water | kJ/kg | 212.7 | 264.8 |
| Condensate return side mother pipe pressure | MPa | 1.52 | 1.44 |
| Temperature of condensate return side mother pipe | ℃ | 11.2 | 36.8 |
| Specific enthalpy of mother pipe at return side of condensed water | kJ/kg | 48.7 | 155.3 |
| Condensed water flow of No. 8 low inlet to high temperature heat exchange system | t/h | 44.33 | 156.30 |
| Condensate flow rate from No. 7 low heating outlet to high-temperature heat exchange system | t/h | 25.50 | 183.83 |
| Condensate releases heat in low-level heat exchange system | MW | 3.18 | 10.35 |
| Side parameter of flue gas | |||
| Ambient temperature | ℃ | 1.8 | 2.7 |
| Relative humidity | % | 96.3 | 84.7 |
| Primary air temperature at inlet of preheater | ℃ | 63.7 | 42.4 |
| Inlet secondary air temperature of preheater | ℃ | 63.6 | 44.6 |
| Cold air temperature of coal feeding mill | ℃ | 14.2 | 16.1 |
| Air weighted average temperature of air preheater inlet | ℃ | 63.6 | 44.1 |
| Weighted average temperature of air entering boiler system boundary | ℃ | 59.0 | 41.5 |
| Actually measured air preheater outlet smoke temperature | ℃ | 151.4 | 144.0 |
| Atmospheric pressure | kPa | 100.7 | 100.5 |
TABLE 3 Heat efficiency test result calculation table for boiler
| Name (R) | Unit of | 320 MW-outage waste heat utilization system |
| Fuel receiving base low calorific value | kJ/kg | 19040 |
| Ambient temperature | ℃ | 2.7 |
| Relative humidity | % | 84.7 |
| Atmospheric pressure | kPa | 100.5 |
| Reference temperature | ℃ | 25 |
| Primary air temperature at inlet of preheater | ℃ | 42.4 |
| Inlet secondary air temperature of preheater | ℃ | 44.6 |
| Cold air temperature of coal feeding mill | ℃ | 16.1 |
| Air weighted average temperature of air preheater inlet | ℃ | 44.1 |
| Weighted average temperature of air entering boiler system boundary | ℃ | 41.5 |
| Combustible content of slag | % | 18.02 |
| Combustible content of fly ash | % | 5.78 |
| Slag proportion | % | 10 |
| Fly ash ratio | % | 90 |
| Actually measured air preheater outlet smoke temperature | ℃ | 144.0 |
| Dry flue gas O of smoke exhaust2Volume percentage content | % | 5.17 |
| Volume percentage of CO in the exhaust smoke | % | 0.00119 |
| Heat loss of exhaust smoke (q)2） | % | 6.19 |
| Incomplete combustion loss of gas (q)3） | % | 0.005 |
| Heat loss due to incomplete combustion of solids (q)4） | % | 1.27 |
| Boiler heat dissipation loss (q)5） | % | 0.18 |
| Physical heat loss of ash (q)6） | % | 0.09 |
| Percentage of external heat to lower heating value of fuel (q)ex） | % | 0.56 |
| Boiler fuel efficiency (ŋ) | % | 92.82 |
| Designed received base low heating value | kJ/kg | 17200 |
| Design ambient temperature | ℃ | 12.7 |
| Design relative humidity | % | 63 |
| Design atmospheric pressure | Pa | 99470 |
| Cold air temperature of coal feeding mill | ℃ | 16.1 |
| Primary air temperature at inlet of preheater | ℃ | 16.1 |
| Inlet secondary air temperature of preheater | ℃ | 7.1 |
| Air weighted average temperature of air preheater inlet | ℃ | 9.0 |
| Weighted average temperature of air entering boiler system boundary | ℃ | 9.7 |
| Exhaust gas temperature after correction of inlet air temperature | ℃ | 153.34 |
| Corrected smoke heat loss (q)2.xz) | % | 6.20 |
| Incomplete combustion loss of gas (q)3.xz) | % | 0.005 |
| Heat loss due to incomplete combustion of solids (q)4.xz) | % | 1.27 |
| Boiler heat dissipation loss (q)5.xz） | % | 0.18 |
| Physical heat loss (q) of the corrected ash6.xz) | % | 0.41 |
| Percentage of external heat to lower heating value of fuel (q)ex) | % | 0 |
| Corrected boiler fuel efficiency (ŋ)xz) | % | 91.935 |
Table 4 table for energy-saving effect correction calculation result of flue gas waste heat deep utilization system
| Parameter name | Unit of | 320 MW-outage waste heat utilization system | 320 MW-commissioning waste heat utilization system |
| Power of generator | MW | 319.88 | 320.43 |
| Test Heat Rate | kJ/(kW·h) | 8128.53 | 8042.54 |
| Parameter corrected generator power | MW | 323.83 | 321.25 |
| Heat rate after parameter correction | kJ/(kW·h) | 8127.92 | 8061.57 |
| Actually measured air preheater outlet smoke temperature | ℃ | 144.0 | 151.4 |
| Exhaust gas temperature after correction of inlet air temperature | ℃ | 153.34 | 127.79 |
| Corrected smoke heat loss (q)2.xz) | % | 6.20 | 4.91 |
| Corrected boiler efficiency | % | 91.935 | 93.225 |
| Efficiency of pipeline | % | 99.0 | 99.0 |
| Rate of service power consumption | % | 6.09 | / |
| Electric power for plant | kW | 19480.7 | / |
| Auxiliary plant electric power added value | kW | / | 353.9 |
| Electric power for plant | kW | / | 19834.6 |
| Rate of service power consumption | % | / | 6.19 |
| Power generation coal consumption after parameter correction | g/(kW·h) | 304.71 | 298.04 |
| Power supply coal consumption after parameter correction | g/(kW·h) | 324.47 | 317.70 |
| Amount of change in heat rate | kJ/(kW·h) | / | -66.35 |
| Amount of change in boiler efficiency | % | / | 1.29 |
| Power coal rate change | g/(kW·h) | / | -6.77 |
Under the working condition of 320MW load, compared with the time of stopping the deep utilization system of the flue gas waste heat, the flue gas waste heat utilization system is put into operation, and under the current operation parameters and the waste heat utilization system adjustment parameters of the unit, the heat consumption rate of the unit after correction is reduced by 66.35kJ/(kW ∙ h), the boiler efficiency after correction is improved by 1.29%, the plant power consumption rate is increased by 0.1%, and the coal consumption of the unit for power supply is reduced by 6.77g/(kW ∙ h).
The embodiment is directed at energy-saving effect calculation analysis of a flue gas waste heat deep utilization system of a 300 MW-grade unit. The deep utilization system for the flue gas waste heat of other capacity units comprises a primary low-pressure economizer and a secondary low-pressure economizer, wherein the primary low-pressure economizer heats condensed water, the condensed water comes from any one low-pressure inlet and outlet, and the condensed water returns to the main condensed water system after being heated; the two-stage low-pressure economizer heats condensed water or closed circulating water, and the heat absorption capacity of the condensed water or the circulating water is used for heating boiler inlet air, so that the energy-saving effect calculation method is suitable for use.
Those not described in detail in this specification are well within the skill of the art.
Although the present invention has been described with reference to the above embodiments, it should be understood that the scope of the present invention is not limited thereto, and that various changes and modifications can be made by those skilled in the art without departing from the spirit and scope of the present invention.
Claims (6)
1. A method for calculating the energy-saving effect of a deep utilization system of flue gas waste heat of a coal-fired boiler is characterized by comprising the following steps of:
the method comprises the following steps: carrying out thermal performance tests of a steam turbine and a boiler under the condition of the shutdown flue gas waste heat deep utilization system, and calculating the test heat consumption rate of the steam turbine set, the corrected heat consumption rate, the test thermal efficiency of the boiler and the corrected thermal efficiency; synchronously measuring the plant power consumption rate of the unit, and measuring the power consumption of a condensate pump of a steam turbine, a booster pump of a flue gas waste heat deep utilization system and a draught fan of a boiler;
step two: under the conditions of the same electric load working condition and the consistency of the host machine operation parameters and the operation mode, performing a thermal performance test of the steam turbine under the working condition of the operating flue gas waste heat deep utilization system, and calculating the test heat consumption rate of the steam turbine and the corrected heat consumption rate; the inlet air temperature of a boiler at the inlet and the outlet of a secondary low-pressure economizer in the flue gas waste heat deep utilization system is synchronously measured, and the power consumption of a steam turbine condensate pump, a flue gas waste heat deep utilization system booster pump and a boiler induced draft fan is measured;
step three: calculating the power consumption change values of a condensate pump, a booster pump and a boiler induced draft fan, and calculating the plant power consumption rate of the unit under the operation condition of the flue gas waste heat deep utilization system;
step four: calculating the power supply coal consumption rate of the unit under the condition by utilizing the heat consumption rate of the steam turbine, the boiler efficiency and the plant power consumption rate of the unit under the shutdown condition of the flue gas waste heat deep utilization system;
step five: correcting the boiler efficiency under the operation stop condition by utilizing the inlet air temperature of the boiler under the operation condition of the flue gas waste heat deep utilization system to obtain the boiler efficiency under the operation condition;
step six: calculating the power supply coal consumption rate of the unit under the working condition by utilizing the heat consumption rate of the steam turbine, the plant power consumption rate of the unit and the boiler efficiency under the working condition of the flue gas waste heat deep utilization system;
step seven: and calculating the reduction value of the unit power supply coal consumption rate under the operation condition of the flue gas waste heat deep utilization system, and taking the reduction value as the energy-saving effect of the flue gas waste heat deep utilization system.
2. The method for calculating the energy-saving effect of the deep utilization system of the flue gas waste heat of the coal-fired boiler according to claim 1, which is characterized by comprising the following steps of:
the specific steps of the first step are as follows:
(1) calculating unit test heat consumption rate H under shutdown working condition of flue gas waste heat deep utilization systemt0The calculation formula is as follows:
Ht0=[Fms0×(hms0-hfw0)+Fcrh0×(hhrh0-hcrh0)+Fgr0×(hms0-hgr0)+Fzr0×(hhrs0-hzr0)]/Pe0
wherein: ht0To test the heat rate, hms0Is the main steam enthalpy, hfw0For the final feed water enthalpy, hhrh0Is the reheat steam enthalpy, hcrh0For the exhaust enthalpy, h, of the high-pressure cylindergr0For reducing the enthalpy of water, h, of the superheaterzr0Reducing the enthalpy of water for reheaters, Fms0Main steam flow, Fcrh0Is the exhaust flow of the high-pressure cylinder, Fgr0For reducing the temperature and water flow of superheater Fzr0For reducing the temperature water flow, P, of the reheatere0Is the power of the generator;
the flow is calculated by the thermodynamic performance test data of the steam turbine, and the enthalpy values of the steam and the water are obtained by measuring the pressure and the temperature of corresponding parts and looking up an enthalpy entropy table;
(2) calculating the corrected heat consumption rate H of the unit under the shutdown condition of the flue gas waste heat deep utilization systemr0The calculation formula is as follows:
Hr0=Ht0/(C10×C20×C30×C40×C50×C60×C70)
wherein Hr0To correct for heat rate, C10、C20、C30、C40、C50、C60、C70The correction coefficients of main steam pressure, main steam temperature, reheat steam loss rate, reheat steam temperature, low-pressure cylinder exhaust steam pressure, superheater desuperheating water flow and reheater desuperheating water flow to heat consumption rate are obtained by checking a correction curve provided by a manufacturing plant; if the superheater attemperation water flow and the reheater attemperation water flow are 0, C in the above formula60=0、C70=0；
(3) Calculating boiler efficiency eta under shutdown working condition of flue gas waste heat deep utilization systemg0The calculation formula is as follows:
ηg0= 100-（q2+q3+q4+q5+q6+qoth-qex）
wherein: etag0For the thermal efficiency of the boiler, q2For heat loss of exhaust gas, q3Heat loss due to incomplete combustion of gas, q4Heat loss due to incomplete combustion of solids, q5For heat loss of boiler, q6Is the physical heat loss of ash, qothFor other heat losses, qexThe percentage of the external heat and the low-level calorific value of the fuel is obtained by a boiler performance test;
the second step comprises the following specific steps:
(1) unit test under operation condition of calculating flue gas waste heat deep utilization systemHeat test rate Ht1The calculation formula is as follows:
Ht1=[Fms1×(hms1-hfw1)+Fcrh1×(hhrh1-hcrh1)+Fgr1×(hms1-hgr1)+Fzr1×(hhrs1-hzr1)]/Pe1
wherein: ht1To test the heat rate, hms1Is the main steam enthalpy, hfw1For the final feed water enthalpy, hhrh1Is the reheat steam enthalpy, hcrh1For the exhaust enthalpy, h, of the high-pressure cylindergr1For reducing the enthalpy of water, h, of the superheaterzr1Reducing the enthalpy of water for reheaters, Fms1Main steam flow, Fcrh1Is the exhaust flow of the high-pressure cylinder, Fgr1For reducing the temperature and water flow of superheater Fzr1For reducing the temperature and water flow rate, P, of the superheatere1Is the power of the generator;
the flow is calculated by the thermal performance test data of the steam turbine under the operation condition of the flue gas waste heat utilization system, the enthalpy values of the steam and the water are obtained by measuring the pressure and the temperature of the corresponding parts and looking up an enthalpy entropy table, and P is kept in the test processe1And Pe0The same;
(2) calculating the corrected heat rate H of the unit under the operation condition of the flue gas waste heat deep utilization systemr1The calculation formula is as follows:
Hr1=Ht1/(C11×C21×C31×C41×C51×C61×C71)
wherein Hr1To correct for heat rate, C11、C21、C31、C41、C51、C61、C71The correction coefficients of main steam pressure, main steam temperature, reheat steam loss rate, reheat steam temperature, low-pressure cylinder exhaust steam pressure, superheater desuperheating water flow and reheater desuperheating water flow to heat consumption rate are obtained by checking a correction curve provided by a manufacturing plant; if the superheater attemperation water flow and the reheater attemperation water flow are 0, C in the above formula61=0、C71=0；
The third step comprises the following specific steps:
(1) calculating the service power rate L under the shutdown condition of the flue gas waste heat deep utilization systemcy0The calculation formula is as follows:
Lcy0 = Pcy0×100/Pe0
wherein L iscy0The plant power rate; pcy0The measured value is the plant power consumption; pe0Testing the measured value for the power of the generator;
(2) calculating the service power rate L under the operation condition of the flue gas waste heat deep utilization systemcy1The calculation formula is as follows:
Lcy1 =（Pcy0+ΔPzyb+ΔPnb+ΔPyfj）×100 / Pe1
wherein L iscy1The plant power rate; delta PzybIncrease the power consumption of the booster pump by delta PnbFor increasing the power consumption of the coagulation pump, Δ PyfjThe power consumption of the induced draft fan is increased by a value, and the data are obtained by actual measurement in the test;
the fourth step comprises the following specific steps:
calculating the unit power supply coal consumption rate b under the shutdown condition of the flue gas waste heat deep utilization system by using the corrected steam turbine heat consumption rate, the boiler efficiency and the unit plant power consumption rate obtained in the first step, the second step and the third stepg0The calculation formula is as follows:
bg0 = Hr0×105/[ηg0×ηgd×7000×4.1868×(1-Lcy0/100)]
wherein eta isgdTaking a design value of 0.99 for pipeline efficiency;
the concrete steps of the fifth step are as follows:
correcting the exhaust smoke temperature by utilizing the inlet air temperature of the boiler at the outlet of the secondary low-pressure economizer under the operation condition of the deep utilization system of the waste heat of the exhaust smoke, and calculating the heat loss of the exhaust smoke by utilizing the exhaust smoke temperature to calculate the corrected boiler efficiency; the correction calculation formula of the exhaust gas temperature is as follows:
θb py=[tb 0×(θ′ ky-θpy)+θ′ ky×(θpy–t0)]/(θ′ ky-t0)
wherein: thetab pyFor conversion to the exhaust gas temperature t at the designed inlet air temperature of the air preheaterb 0For designed air preheater inlet air temperature theta′ kyFor actually measuring the inlet flue gas temperature theta of the air preheaterpyFor actually measuring the outlet flue gas temperature t of the air preheater0Actually measuring the air temperature at the inlet of the air preheater;
designed inlet air temperature tb 0And the converted exhaust gas temperature thetab pyAnd boiler input heat respectively replaces t in the calculation formula of the heat loss of the exhaust smoke in GB 10184-20150And thetapyAnd obtaining the corrected heat loss q of exhaust gas2Substituting the formula into the formula in the step (3), and calculating to obtain the corrected boiler thermal efficiency;
the sixth step comprises the following specific steps:
calculating the unit power supply coal consumption rate b when the flue gas waste heat deep utilization system is put into operation by using the corrected heat consumption rate, the corrected boiler efficiency and the unit plant power consumption rate of the steam turbine under the operating condition of the flue gas waste heat deep utilization system obtained in the second step, the third step and the fifth stepg1The calculation formula is as follows:
bg1 = Hr1×105/[ηg1×ηgd×7000×4.1868×(1-Lcy1/100)]
the concrete steps of the seventh step are as follows:
energy-saving effect of flue gas waste heat deep utilization system is with reduction value delta b of unit power supply coal consumption rate after commissioninggExpressed, the calculation formula is:
Δbg =bg0 - bg1。
3. the method for calculating the energy saving effect of the deep flue gas waste heat utilization system of the coal-fired boiler according to claim 1 or 2, characterized in that the deep flue gas waste heat utilization system is arranged behind an air preheater of a tail flue of the boiler, the deep flue gas waste heat utilization system comprises a primary low-pressure economizer and a secondary low-pressure economizer, the primary low-pressure economizer heats condensed water, the secondary low-pressure economizer heats condensed water or closed circulating water, and the condensed water or closed circulating water is used for heating inlet air of the boiler.
4. The method for calculating the energy-saving effect of the deep flue gas waste heat utilization system of the coal-fired boiler according to claim 1 or 2, characterized in that when the operation and shutdown conditions of the deep flue gas waste heat utilization system are switched, the load and main operation parameters of a main engine are kept unchanged, the operation mode of the main engine is unchanged, and the operation mode of a unit thermodynamic system except the deep flue gas waste heat utilization system is unchanged.
5. The method for calculating the energy-saving effect of the deep flue gas waste heat utilization system of the coal-fired boiler according to claim 1 or 2, characterized in that a boiler efficiency test is only performed once, a secondary low-pressure economizer of the deep flue gas waste heat utilization system influences the inlet air temperature of the boiler, only the influence of the inlet air temperature on the boiler efficiency is corrected, and the influence of the error of the boiler test system is eliminated.
6. The method for calculating the energy-saving effect of the deep flue gas waste heat utilization system of the coal-fired boiler according to claim 1 or 2, characterized in that only the plant power consumption rate under the operation or shutdown condition is measured, the power consumption of a steam turbine condensate pump, a flue gas waste heat deep utilization system booster pump and a boiler induced draft fan under two conditions is measured, the plant power consumption rate after the condition switching is calculated by using the change values of the power consumption of three auxiliary machines, and the influence of changes such as the operation modes and states of other auxiliary machines on the test error is eliminated.
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| CN118135772A (en) * | 2024-05-08 | 2024-06-04 | 江西赣能股份有限公司 | Method and system for monitoring and alarming running state of equipment in thermal power plant |
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| CN116703086A (en) * | 2023-06-06 | 2023-09-05 | 中国电力建设工程咨询有限公司 | Coal saving method and system based on flue gas recovery system |
| CN118135772A (en) * | 2024-05-08 | 2024-06-04 | 江西赣能股份有限公司 | Method and system for monitoring and alarming running state of equipment in thermal power plant |
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