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US20080057451A1 - Boiler and combustion control method - Google Patents

Boiler and combustion control method Download PDF

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Publication number
US20080057451A1
US20080057451A1 US11/882,747 US88274707A US2008057451A1 US 20080057451 A1 US20080057451 A1 US 20080057451A1 US 88274707 A US88274707 A US 88274707A US 2008057451 A1 US2008057451 A1 US 2008057451A1
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United States
Prior art keywords
fuel
air
burner
temperature
air quantity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/882,747
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English (en)
Inventor
Tatsuya Fujiwara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Miura Co Ltd
Original Assignee
Miura Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Assigned to MIURA CO., LTD. reassignment MIURA CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUJIWARA, TATSUYA
Publication of US20080057451A1 publication Critical patent/US20080057451A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/02—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F23N3/002—Regulating air supply or draught using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/04—Regulating fuel supply conjointly with air supply and with draught
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K2400/00—Pretreatment and supply of gaseous fuel
    • F23K2400/20—Supply line arrangements
    • F23K2400/201—Control devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K2900/00—Special features of, or arrangements for fuel supplies
    • F23K2900/05001—Control or safety devices in gaseous or liquid fuel supply lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F23N2225/20—Measuring temperature entrant temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2233/00—Ventilators
    • F23N2233/06—Ventilators at the air intake
    • F23N2233/08—Ventilators at the air intake with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2241/00—Applications
    • F23N2241/04—Heating water

Definitions

  • the present invention relates to a boiler and a combustion control method making it possible to perform combustion at a predetermined air ratio and to suppress generation of NOx in the exhaust gas.
  • JP 2001-272030 A proposes an air-fuel ratio control (air ratio control) monitoring method for a burner in a boiler and an air-fuel ratio control monitoring apparatus for executing the method.
  • the pressure of the combustion air to be supplied to the burner and the pressure of the fuel to be supplied to the burner or the pressure of the fuel returned from the burner are monitored to make a judgment as to whether the air amount and the fuel amount are being properly controlled.
  • JP 10-47654 A discloses an air ratio automatic correction system for a combustion apparatus in which combustion air is preheated and supplied.
  • each of a combustion air supply path and a fuel supply path is provided with a pressure gauge and a thermometer
  • the fuel supply path is equipped with an equalizing valve for equalizing the fuel supply pressure and the combustion air supply pressure
  • an impulse line of the equalizing valve is provided with an orifice and a bleeding valve
  • a fuel supply pressure for supplying the requisite fuel for maintaining a predetermined air ratio is obtained from the actual air temperature and air supply pressure and fuel temperature measured by each thermometer and pressure gauge, and the fuel supply pressure thus obtained and the actually measured fuel supply pressure are compared with each other to adjust the bleeding valve such that those become equal to each other.
  • JP 2000-46302 A discloses a boiler in which there is provided a rectangular combustion space with vertical water tubes standing close together between water tube walls arranged in parallel so as to be spaced apart from the burner front surface.
  • a relatively long gas passage extending from the burner to a gas outlet via the inter-space between the vertical water tubes, thereby suppressing the flame combustion temperature to a level of A approximately 1200 to 1300° C. to thereby reduce NOx to 70 to 80 ppm and to reduce CO to 50 ppm or less.
  • the boiler as proposed in JP 2000-46032 A can effectively achieve a reduction in NOx.
  • the boiler capable of achieving a further reduction in NOx generation in a stable manner.
  • a boiler according to the present invention includes: a control means for adjusting a quantity of air to be used for combustion based on a temperature change in an air and fuel to be used for combustion. Further, a boiler according to the present invention includes: a burner; a fuel supply means for supplying fuel to the burner; a blowing means for supplying air to the burner; and an amount of fuel to be supplied to the burner and a quantity of air to be supplied to the burner, which are adjusted by the control means, in which the control means has a reference amount computing portion for calculating a reference fuel amount and a reference air quantity to be supplied to the burner with respect to a required load, an air quantity computing portion that corrects the reference air quantity based on a temperature of the air to be supplied to the burner and a temperature of the fuel to be supplied to the burner and calculates the corrected air quantity as a supply air quantity, and a control portion that controls combustion at the burner based on the reference fuel amount and the supply air quantity.
  • thermistors are preferably used as a means for measuring the temperature of the air to be supplied to the burner and as a means for measuring the temperature of the fuel to be supplied to the burner.
  • the air quantity computing portion calculates the supply air quantity such that a correction amount for correcting the reference air quantity is in proportion to 1/(1+R TH1 /R s +R TH1 /R TH2 ), where R TH1 is a resistance value of an air temperature measuring thermistor, R TH2 is a resistance value of a fuel temperature measuring thermistor, and R s is a resistance value of a fixed resistor.
  • the air quantity computing portion calculates the supply air quantity such that a correction amount for correcting the reference air quantity is in proportion to T a /(T g ) 1/2 , where T g is the temperature of the fuel measured by a fuel temperature measuring means, and T a is the temperature of the air measured by an air temperature measuring means.
  • a combustion control method is a method by which combustion is performed at a predetermined air ratio and in which NOx in an exhaust gas is suppressed to a level within a predetermined range, the combustion control method including: calculating a reference fuel amount and a reference air quantity corresponding to a required load of the boiler; correcting the calculated reference air quantity based on temperatures of a fuel and an air to be used for combustion; and performing combustion with the corrected air quantity and the reference fuel amount.
  • the boiler according to the present invention has a relatively simple construction, and is capable of performing combustion at a predetermined air ratio, suppressing generation of NOx in the exhaust gas in a stable manner, and performing stable combustion with high thermal efficiency. Further, according to the combustion control method of the present invention, it is possible to suppress generation of NOx to a level of 12 ppm or less in normal combustion.
  • FIG. 1 is a schematic view of the construction of a boiler according to the present invention
  • FIG. 2 is a circuit diagram showing a construction example of a blower control portion of a control device of the boiler of FIG. 1 ;
  • FIG. 3 is a graph showing an example of how the O 2 amount in the exhaust gas is controlled by a control device having the blower control portion of FIG. 2 ;
  • FIG. 4 is a graph showing the relationship between ambient temperature and fuel temperature
  • FIG. 5 is a graph showing an example of how the NOx amount in the exhaust gas is controlled by the control device having the blower control portion of FIG. 2 ;
  • FIG. 6 is a graph showing the relationship between the NOx amount and the O 2 amount in the exhaust gas
  • FIG. 7 is a graph showing the relationship between blower frequency and supply air temperature when the control device having the blower control portion of FIG. 2 is used;
  • FIG. 8 is a graph showing the relationship between the O 2 amount in the exhaust gas and fuel temperature when the control device having the blower control portion of FIG. 2 is used and when the supply air temperature is fixed at 20° C. or 40° C.;
  • FIG. 9 is a graph showing the relationship between the O 2 amount in the exhaust gas and fuel temperature when, in the case of FIG. 8 , fixed resistance R s , reference frequency f 0 , and maximum frequency f m are varied.
  • FIG. 1 is a schematic view of an embodiment thereof. As shown in FIG.
  • a boiler 100 has a burner 5 , a fuel supply device 10 for supplying fuel to the burner 5 , a blowing device 20 for supplying air to the burner 5 , and a control device 30 for controlling the amount of fuel supplied to the burner 5 and the quantity of air supplied to the burner 5 ; further, the boiler 100 has a fuel temperature measuring device 35 for measuring the temperature of the fuel supplied to the burner 5 and transmitting a corresponding signal to the control device 30 , and an air temperature measuring device 36 for measuring the temperature of the air supplied to the burner 5 and transmitting a corresponding signal to the control device 30 .
  • the boiler 100 operates as follows: Fuel (e.g., natural gas) is sent from the fuel supply device 10 and spouted at the forward end of the fuel supply device 10 (in the vicinity of the right-hand end of the fuel supply device 10 as seen in FIG. 1 ); this fuel is supplied to the burner 5 while being mixed with combustion air supplied from the blowing device 20 , and is burned by the burner 5 .
  • the burned gas passes gaps between a plurality of water tubes (water tube group) 40 , and is gradually cooled while performing heat exchange with water in the plurality of water tubes 40 , and is then sent to a flue 50 before being discharged into the atmosphere.
  • burner 5 It is possible to use a well-known burner as the burner 5 . There are no particular limitations regarding the type of burner. In the case of the boiler of the embodiment shown in FIG. 1 , there is used a perfectly premixed burner having a planar burning surface.
  • the fuel supply device 10 it is possible to use a well-known fuel supply device.
  • a fuel supply device having a pump, a control valve, and a control device for controlling them, and capable of supplying a predetermined amount of fuel corresponding to a load.
  • blowing device 20 It is possible to use a well-known blowing device as the blowing device 20 .
  • a well-known blowing device for example, it is possible to use an inverter type blower having a blower, a drive source, and an inverter for controlling the RPM of the blower, and capable of supplying a predetermined quantity of air corresponding to the fuel. It is also possible to use a so-called damper type blower capable of supplying a predetermined quantity of air corresponding to the fuel.
  • the control device 30 has a reference amount computing portion, an air quantity computing portion, and a control portion.
  • the reference amount computing portion serves to calculate a reference fuel amount and a reference air quantity corresponding to the load required of the boiler 100 by the heat engine.
  • the air quantity computing portion serves to correct a reference air quantity calculated by the reference amount computing portion based on the output from an air temperature measuring device 36 for measuring the temperature of the air to be supplied to the burner 5 and the output from a fuel temperature measuring device 35 for measuring the temperature of the fuel to be supplied to the burner 5 , calculating the corrected air quantity as the supply air quantity.
  • the control portion serves to supply the burner 5 with the quantity of supply air as obtained by the air quantity computing portion with respect to the reference fuel amount already calculated to perform required combustion.
  • the fuel temperature measuring device 35 and the air temperature measuring device 36 are capable of measuring the temperatures of the fuel and the air and supplying the control device 30 with signals corresponding to the temperatures.
  • a thermistor as the fuel temperature measuring device 35 or the air temperature measuring device 36 , whereby it is possible to form the fuel temperature measuring device 35 or the air temperature measuring device 36 in a simple and compact structure.
  • the boiler 100 constructed as described above, is used as follows. First, when a certain amount of load is required of the boiler 100 by the heat engine or the like, the reference amount computing portion of the control device 30 calculates a reference fuel amount and a reference air quantity with respect to the required load. The reference fuel amount and the reference air quantity are theoretically computed under a predetermined air ratio. Next, the calculated reference air quantity is corrected by the air quantity computing portion based on the temperatures of the fuel and the air to be supplied to the burner 5 .
  • control device 30 serves to supply the burner 5 with a corrected air quantity described below based on the theoretical reference fuel amount and the temperatures of the actually supplied fuel and air, making it possible to perform the required combustion.
  • this reference air quantity is corrected according to a principle described below.
  • an inverter type blower is used as the blowing device 20 .
  • the temperature of the air supplied to the burner 5 (supply air temperature) is T a
  • the air density is ⁇ a
  • the volume flow rate is Q a
  • the RPM of the blower is N. Since the volume flow rate Q a is in proportion to the RPM N, and the air density ⁇ a is in inverse proportion to the supply air temperature T a , the following formula (1) holds true:
  • the fuel is supplied to the burner 5 such that the flow velocity of the fuel supplied is a predetermined flow velocity, that is, the difference in pressure between the pressurization source side and the boiler 100 side is fixed, so the following equation holds true:
  • ⁇ P g is the difference in pressure
  • T g is the fuel temperature
  • ⁇ g is the fuel density
  • N k ⁇ T a /(T g ) 1/2 (4)
  • Equation (4) shows that it is possible to perform combustion at a fixed air ratio by making an adjustment such that the RPM of the blower is in proportion to the supply air temperature T a and in inverse proportion to (T g ) 1/2 , where T g is the fuel temperature. That is, by supplying the burner 5 with a quantity of air (supply air quantity) corrected by taking into consideration the reference air quantity and the supply air temperature, it is possible to cause the boiler 100 to perform combustion at a predetermined air ratio.
  • the pressure of the air supplied to the burner 5 is not necessarily an essential monitoring factor for performing combustion at a fixed air ratio. During use of the boiler, there are various fluctuations in conditions, and it can happen that the predetermined air ratio is deviated from. In such cases, it is effective to monitor the air pressure.
  • the reference air quantity is corrected based on the supply air temperature and the fuel temperature, and the corrected air quantity (supply air quantity) and the already calculated reference fuel amount are supplied to the burner 5 by the control portion of the control device 30 to thereby perform combustion.
  • the correction amount for the correction of the reference air quantity is an amount in proportion to T a /(T g ) 1/2 .
  • This correction of the reference air quantity based on the supply air temperature and the fuel temperature can be executed by providing in the air quantity computing portion a program allowing computation of a predetermined correction amount based on the signals from the fuel temperature measuring device 35 and the air temperature measuring device 36 , and a computer for executing the program.
  • a control device 30 of a simple structure by a control device having the fuel temperature measuring device 35 and the air temperature measuring device 36 consisting of thermistors, and a blower control portion capable of directly controlling the blower based on signals from the thermistors.
  • FIG. 2 shows an example of the blower control portion of the control device 30 .
  • the blower control portion of the control device 30 has a fixed resistor R s , a fuel temperature measuring thermistor R TH2 connected in parallel thereto, and an air temperature measuring thermistor R TH1 connected in series to them.
  • the symbols represented by R and their subscripts indicate resistance values ( ⁇ ).
  • FIG. 3 shows the O 2 amount in the exhaust gas when the boiler 100 is controlled by the control device 30 having the blower control portion shown in FIG. 2 .
  • the horizontal axis indicates the supply air temperature
  • the vertical axis indicates the O 2 amount in the exhaust gas.
  • curves A 1 and A 2 represent examples of the present invention in which combustion is performed in the boiler 100 with the supply air quantity and the reference fuel amount.
  • the curve A 1 indicates the case in which the supply air quantity is obtained on the assumption that the fuel temperature and the supply air temperature are equal to each other.
  • the curve A 2 indicates the case in which the supply air quantity is obtained on the assumption that the fuel temperature changes in a proportion of 1 ⁇ 2 with respect to the change amount of the supply air temperature.
  • Curve B indicates a case (conventional example) in which it is assumed that the supply air temperature and the fuel temperature are equal to each other and in which combustion is performed in the boiler 100 with an air quantity obtained by correcting the reference air quantity taking solely the supply air temperature into consideration and the reference fuel amount.
  • the reference frequency f o is 50 Hz, and the maximum frequency f m is 73 Hz.
  • the curves A 1 and A 2 are of a fixed linear configuration, with the O 2 amount being 6%.
  • combustion is performed at a fixed air ratio in the supply air temperature range of 10 to 50° C.
  • the curve B is an inclined straight line indicating a change in O 2 amount of 5.7 to 6.7% within the supply temperature range of 10 to 50° C.
  • combustion at a fixed air ratio is not performed within the temperature range of 10 to 50° C. in the case of the conventional example.
  • the curve A 1 is a graph indicating the case in which the supply air quantity is obtained on the assumption that the fuel temperature and the supply air temperature are equal to each other
  • the curve A 2 is a graph indicating the case in which the supply air quantity is obtained on the assumption that the proportion of the change in fuel temperature is 1 ⁇ 2 of the proportion of the change in supply air temperature.
  • the O 2 amount can be controlled to a value within the range surrounded by the curves A 1 and A 2 .
  • FIG. 4 is a graph showing the relationship between the temperature around piping and the fuel temperature at the inlet of the boiler 100 in a case in which fuel (natural gas or LPG) flows through the piping, which has a total length of approximately 50 m and is exposed on the ground, at a maximum flow velocity of approximately 500 Nm 3 /h.
  • the horizontal axis indicates the ambient temperature
  • the vertical axis indicates the fuel temperature.
  • the fuel temperature changes at a proportion of 3 ⁇ 4 with respect to the change amount of the ambient temperature.
  • the fluctuation width of the fuel temperature at the inlet of the boiler 100 is approximately 1 ⁇ 2 of the fluctuation width of the ambient temperature.
  • the fluctuation width of the fuel temperature at the inlet of the boiler 100 is generally approximately 1 ⁇ 2 or less of the fluctuation width of the ambient temperature.
  • the supply air temperature is substantially equal to the ambient temperature. That is, in the present invention, it is to be assumed that the O 2 amount can be controlled within the range surrounded by the curves A 1 and A 2 shown in FIG. 3 .
  • FIG. 5 is a graph showing the relationship between the supply air temperature and the NOx generation amount.
  • the horizontal axis indicates the supply air temperature
  • the vertical axis indicates the NOx amount (ppm).
  • the curves shown in FIG. 5 are obtained by converting the O 2 amounts of the curves A 1 , A 2 and B shown in FIG. 3 into NOx amounts based on the characteristic curve of FIG. 6 showing the relationship between the NOx amount and the O 2 amount.
  • FIG. 6 is a graph obtained through a combustion test on a surface combustion burner type boiler 100 using premixed air fuel mixture with a performance of an evaporation amount of 3130 kg/h.
  • the symbols A 1 , A 2 and B indicate examples of the present invention
  • the symbol B indicates a conventional example.
  • the symbol A 1 indicates a case in which the supply air quantity is obtained on the assumption that the fuel temperature is equal to the supply air temperature
  • the symbol A 2 indicates a case in which the supply air quantity is obtained on the assumption that the proportion of the change in the fuel temperature is 1 ⁇ 2 of the proportion of the change in the supply air temperature. This also applies to the following description.
  • the NOx amount is 10.6 to 11.2 ppm within the supply air temperature range of 10 to 50° C.
  • the NOx amount is kept at a level below 12 ppm.
  • FIG. 7 is a graph showing the relationship between the control frequency and the supply air temperature in an inverter type blower under the same conditions as in the case of the graph shown in FIG. 2 or 3 .
  • the horizontal axis indicates the supply air temperature
  • the vertical axis indicates the frequency of the blower.
  • the curves A 1 , A 2 and B are all substantially linear, with the curve A 1 exhibiting the minimum gradient and the curve B the maximum gradient. From the results as shown in FIG. 7 and those shown in FIG. 3 , it can be seen that in the case of the conventional example, an excessive quantity of air is supplied to the burner 5 upon an increase in the supply air temperature. That is, it can be seen that in the present invention, not only is it possible to perform combustion in the boiler 100 at a fixed air ratio and with low NOx, but it is also possible to perform an economical operation with the boiler 100 .
  • the boiler 100 having the control device 30 can perform combustion within a supply temperature range of 10 to 50° C., at a fixed air ratio, and with low NOx.
  • the room temperature is generally higher than the outside temperature, with its upper limit being approximately 50° C.
  • the supply air temperature is outside the above-mentioned range in some cases. Such cases can be coped with by selecting a fixed resistor and a thermistor that are in conformity with the conditions of use thereof.
  • FIGS. 8 and 9 show the results of an examination of the effects of the fixed resistance R s , the reference frequency f o of the inverter, and the maximum frequency f m on the O 2 amount in the exhaust gas when the supply air temperature is fixed at 20° C. or 40° C.
  • the horizontal axis indicates the fuel temperature
  • the vertical axis indicates the O 2 amount (ppm) in the exhaust gas.
  • the supply air temperature is 20° C. or 40° C.
  • the fixed resistance R s , the reference frequency f o , and the maximum frequency f m are the same as those of FIG. 3 .
  • the fixed resistance R s is 3000 ⁇
  • the reference frequency f o is 51 Hz
  • the maximum frequency f m is 74 Hz.
  • the curve B indicates a conventional case.
  • FIGS. 8 and 9 shows that in the case of FIG. 8 , the O 2 amount in the exhaust gas is controlled to a fixed level, and that in the case of FIG. 9 , no conspicuous effect of the control is to be observed. That is, it can be seen that it is necessary to select the fixed resistance R s , the thermistor resistors R TH1 and R TH2 , the reference frequency f o of the inverter, and the maximum frequency f m according the conditions of use of the boiler 100 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Control Of Combustion (AREA)
US11/882,747 2006-08-30 2007-08-03 Boiler and combustion control method Abandoned US20080057451A1 (en)

Applications Claiming Priority (2)

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JP2006-234371 2006-08-30
JP2006234371A JP2008057841A (ja) 2006-08-30 2006-08-30 ボイラおよびボイラの燃焼方法

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JP (1) JP2008057841A (zh)
KR (1) KR20080020493A (zh)
CN (1) CN101135460A (zh)
CA (1) CA2599516A1 (zh)
TW (1) TW200811403A (zh)

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US20120115096A1 (en) * 2009-05-20 2012-05-10 Costanzo Gadini Device for controlling gas supply to a burner
CN103383112A (zh) * 2013-08-05 2013-11-06 大唐信阳发电有限责任公司 一种给水泵汽轮机控制方法和系统
BE1024418B1 (fr) * 2015-12-18 2018-02-16 Robert Bosch Gmbh Dispositif d'appareil de chauffage
US11421876B2 (en) * 2018-08-30 2022-08-23 Bosch Termotecnologia S.A. Method for regulating a heating device and heating device
CN119468248A (zh) * 2024-12-13 2025-02-18 扬州市银焰机械有限公司 一种悬浮窑用燃烧器智能控制系统及其方法

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JP5800226B2 (ja) * 2011-09-29 2015-10-28 三浦工業株式会社 ボイラ
CN102353072B (zh) * 2011-10-24 2013-08-21 云南航天工业总公司 一种柴油燃烧器输出功率的控制方法及其控制装置
CN104534503A (zh) * 2014-12-23 2015-04-22 云南航天工业有限公司 一种柴油燃烧器的海拔、温度自修正控制方法
CN106642192B (zh) * 2017-02-17 2019-01-15 长沙市驱动源电气技术有限公司 震动式给料燃烧机及其控制方法
CN109519962B (zh) * 2018-12-28 2023-12-01 启明星宇节能科技股份有限公司 锅炉低氮燃烧风量调节设备

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US20100275653A1 (en) * 2009-05-01 2010-11-04 Owens-Brockway Glass Container Inc. System and Method for Controlling Temperature in a Forehearth
US8191387B2 (en) 2009-05-01 2012-06-05 Owens-Brockway Glass Container Inc. System and method for controlling temperature in a forehearth
US8549883B2 (en) 2009-05-01 2013-10-08 Owens-Brookway Glass Container Inc. System and method for controlling temperature in a forehearth
US20120115096A1 (en) * 2009-05-20 2012-05-10 Costanzo Gadini Device for controlling gas supply to a burner
US9347665B2 (en) * 2009-05-20 2016-05-24 Eltek S.P.A. Device for controlling gas supply to a burner
CN103383112A (zh) * 2013-08-05 2013-11-06 大唐信阳发电有限责任公司 一种给水泵汽轮机控制方法和系统
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US11421876B2 (en) * 2018-08-30 2022-08-23 Bosch Termotecnologia S.A. Method for regulating a heating device and heating device
CN119468248A (zh) * 2024-12-13 2025-02-18 扬州市银焰机械有限公司 一种悬浮窑用燃烧器智能控制系统及其方法

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KR20080020493A (ko) 2008-03-05

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