EP2037176A2 - Procédé de commande d'un brûleur à évaporation - Google Patents

Procédé de commande d'un brûleur à évaporation Download PDF

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Publication number
EP2037176A2
EP2037176A2 EP08105288A EP08105288A EP2037176A2 EP 2037176 A2 EP2037176 A2 EP 2037176A2 EP 08105288 A EP08105288 A EP 08105288A EP 08105288 A EP08105288 A EP 08105288A EP 2037176 A2 EP2037176 A2 EP 2037176A2
Authority
EP
European Patent Office
Prior art keywords
correction factor
temperature
heating power
fuel
int
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.)
Granted
Application number
EP08105288A
Other languages
German (de)
English (en)
Other versions
EP2037176A3 (fr
EP2037176B1 (fr
Inventor
Josef Wueest
Erwin Schlup
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.)
GLUTZ AG
Original Assignee
Thermmix AG
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
Application filed by Thermmix AG filed Critical Thermmix AG
Publication of EP2037176A2 publication Critical patent/EP2037176A2/fr
Publication of EP2037176A3 publication Critical patent/EP2037176A3/fr
Application granted granted Critical
Publication of EP2037176B1 publication Critical patent/EP2037176B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F23N5/12—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium using ionisation-sensitive elements, i.e. flame rods
    • F23N5/123—Systems for controlling combustion using devices responsive to thermal changes or to thermal expansion of a medium using ionisation-sensitive elements, i.e. flame rods 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
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/022—Regulating fuel supply conjointly with air supply using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2223/00—Signal processing; Details thereof
    • F23N2223/42—Function generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F23N2225/16—Measuring temperature burner 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
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/30—Pumps

Definitions

  • the invention relates to a method for controlling an evaporator burner of the type mentioned in the preamble of claim 1.
  • Such an evaporator burner is designed for the combustion of liquid fuels such as commercial heating oil of various qualities or kerosene and is particularly suitable for heating systems of residential buildings, but also of non-residential buildings, where a rather low heating power in the range of a few kilowatts is sufficient.
  • the heat generated by the burner when burning the fuel for example, heats water in a boiler.
  • the liquid fuel is vaporized under heat, mixed with air and then burned.
  • An evaporator burner referred to in the preamble of claim 1 is known from the WO 00/12935 known.
  • the evaporator burner is located below the boiler.
  • the evaporator chamber is electrically preheated at the start of the burner. As soon as the flame burns, the evaporator chamber is then heated by the hot combustion gases flowing past the evaporator chamber, which is achieved by means of a deflecting collar. Once the evaporator chamber has reached a predetermined temperature, which is monitored by means of a temperature sensor, the electric heater can be turned off.
  • This evaporator burner is designed as a tumble burner and is mounted on top of the boiler. The flame burns below the evaporator chamber. The rising hot combustion gases heat the evaporator chamber directly.
  • evaporator burners are designed as modulating burners, i. Their heating power can be steplessly controlled in a predetermined work area.
  • the evaporation of the fuel is extremely important. So the temperature of the evaporator chamber must be high enough for the fuel to evaporate completely.
  • the amount of air supplied must be adapted to the amount of fuel supplied. If more air is supplied than is needed for the combustion, then this reduces the efficiency. If less air is supplied than is needed for the combustion, then this increases on the one hand the exhaust emissions and on the other hand leads to the deposition of unburned or not completely burned fuel residues.
  • the invention has for its object to develop a method for the optimal operation of such an evaporator burner, without measuring devices for measuring the amount of air supplied and the supplied amount of fuel manages.
  • the Fig. 1 shows a vertical section through the necessary for the understanding of the invention parts of such designed as a tumble burner evaporator burner.
  • the evaporator burner comprises an evaporator chamber 1, a blower 2, an electric motor 3 for driving the blower 2, an atomizer cup 4, a mixing wheel 5 and a flame holder 6.
  • the flame burns on the outer wall of the flame holder 6.
  • the blower 2 comprises two rotors 8 and 9, which are mounted on a drive shaft 7 driven by the motor 3.
  • the rotors 8, 9 convey fresh air into the evaporator chamber 1.
  • the flame holder 6 contains a lid and rests on the evaporator chamber 1.
  • the evaporator chamber 1 is a chamber open to the flame holder 6 with a bottom 10 and a side wall 11. The space enclosed by the bottom 10 and the side wall 11 of the evaporator chamber 1 space forms a mixing and evaporator zone.
  • an electric heater 12 is integrated in the wall of the evaporator chamber 1, in the wall of the evaporator chamber 1, an electric heater 12 is integrated.
  • the atomizer cup 4 and the mixing wheel 5 are also mounted on the drive shaft 7 in this embodiment, ie the atomizer cup 4, the mixing wheel 5 and the rotors 8, 9 of the fan 2 rotate together at the same speed.
  • the atomizer cup 4 and the mixing wheel 5 could also be driven separately.
  • a fuel pump 13 delivers liquid fuel through a fuel line 14, which projects into the atomizer cup 4.
  • the pumped fuel flows or drips onto the inner wall of the atomizer cup 4. Due to the rotation of the atomizer cup 4, the fuel flows against the outer edge of the atomizer cup 4 under the action of centrifugal force, is thrown off the edge and impinges on the inner wall of the evaporator chamber 1. Simultaneously 2 fresh air is conveyed by the rotors 8, 9 of the blower.
  • a certain proportion of the fresh air flows outside the atomizer cup 4 along directly into the evaporator chamber 1, another portion of the fresh air passes through openings in the bottom of the Atomizer cup 4 into the interior of the atomizer cup 4 and the mixing wheel 5.
  • the rotating mixing wheel 5 serves to redirect the supplied fresh air into the evaporator chamber 1, to swirl and to mix with the evaporated fuel oil vapor.
  • Such an evaporator burner can be designed as a tumble burner as shown, but it can also be designed for any other installation position, for example, a horizontal mounting position. It is suitable for use with condensing boilers as well as boilers of other types.
  • the evaporator burner is a modulatable burner, in which the heating power P between a low load value P min and a nominal load value P max can be varied continuously or in stages.
  • the low load value P min is typically about 30 to 35% of the rated load value P max .
  • the evaporator burner is mounted on a boiler whose water temperature is controlled by a heating controller.
  • the heating controller requires from the evaporator burner a heating power P which is in the range between P min + k * (P max -P min ), wherein the size k denotes the degree of modulation of the evaporator burner and assumes values between 0 and 1.
  • the requested heating power P changes continuously according to the current heat demand.
  • the commissioning of the burner comprises in a known manner the switching on of the electric heater 12 of the evaporator chamber 1. As a result, the temperature of the evaporator chamber 1 increases. Once the temperature of the evaporator chamber 1 has reached a predetermined value, the combustion chamber is vented, then adjusted the speed of the fan 2 of the set ignition power and finally started the fuel supply to the burner. On the outer wall of the flame holder 6 is then formed by an ignition, the flame. As a result, now the evaporator chamber 1 is further heated by the heat developed by the flame, so that the temperature of the evaporator chamber 1 further increases. Once the temperature of the evaporator chamber 1 has reached a predetermined value, the electric heater 12 of the evaporator chamber 1 is turned off.
  • the function g (P) is a function indicating at which speed the fan 2 must rotate, when the burner has to supply the heating power P. It is set so that the temperature of the evaporator chamber 1 under ideal operating conditions and without application of the correction factor K (P) at the heating power P min reaches a predetermined value T VDKmin increases linearly with increasing heating power and at the maximum heating power P max a predetermined value T VDKmax reached.
  • a function g (P) has proven itself, which, as in the Fig. 2 is shown by two straight lines G 1 and G 2 with different pitch can be displayed.
  • the setpoint T S (P) is a function dependent only on the heating power P.
  • the Fig. 3 shows the dependence of the setpoint T S of the heating power P and the modulation depth k for a developed by the applicant evaporator burner.
  • the internal setpoint value T int (t) serves to simulate the effective behavior of the actual temperature of the evaporator chamber 1. It depends on the course of business. If the requested heating power P suddenly abruptly changes, then the setpoint T S (P) also changes abruptly, while the internal setpoint T int (t) is tracked to the setpoint T S via a power-dependent low-pass filter. Measurements have shown that the internal setpoint value T int (t) is advantageously tracked according to an e-function with a predetermined time constant adapted to the burner.
  • T int ⁇ t n + 1 T int t n + ⁇ * T S ⁇ k ⁇ t n + 1 - T int t n
  • ⁇ is set so that the course of the internal target value T int simulates the course of the actual temperature of the evaporator chamber 1 as well as possible during a power change.
  • the internal setpoint T int (t) is at a predetermined frequency f 1 of, for example, 0.1 Hz, ie every 10th
  • the correction factor K (P) is a factor that serves to minimize deviations from the ideal air / fuel ratio.
  • the causes of such deviations are manifold, on the one hand there are external factors such as the weather conditions (air pressure, humidity, etc.) and internal factors such as the degree of contamination of the evaporator chamber, etc.
  • the correction factor K is therefore constantly updated during operation.
  • the Fig. 4 shows the dependence of the correction factor K on the heating power P and the degree of modulation k.
  • K 1 and K 2 denote two interpolation point values, namely K 1 a reference point value for low load and K 2 a reference point value for nominal load.
  • the correction factor K should be increased by a value appropriate to the amount of the temperature difference ⁇ T. As a result, the rotational speed D of the blower 2 and thus the air supply is increased. If the temperature difference ⁇ T is less than 0, it means that the evaporator chamber 1 is too cold. Therefore, the correction factor K should be reduced by a value appropriate to the amount of the temperature difference ⁇ T.
  • the change of the correction factor K can be made in various ways.
  • a first possibility is to increase or decrease both interpolation point values K 1 and K 2 by an equal value ⁇ k ( ⁇ T), the function ⁇ k ( ⁇ T) being a predetermined function. Because disturbing changes in the environmental conditions (eg soiling of the boiler, etc.) on the Operation at low load and under heavy load have different effects, the correction values for low load and high load are advantageously tracked separately.
  • a second, preferred option is therefore to change the two interpolation values by different values and this in function of the current heating power.
  • the interpolation point value K 2 (t n + 1 ) is limited to values within the predetermined range B 1 ... B 2 . This ensures that the correction factor K is within the predetermined range B 1 ... B 2 .
  • K ⁇ P ⁇ t n + 1 K 1 ⁇ t n + 1 + k * K 2 ⁇ t n + 1 - K 1 ⁇ t n + 1
  • the two interpolation points K 1 and K 2 are performed as time-dependent parameters like the internal reference value T int and recalculated periodically but with different frequencies.
  • the update of the correction factor K can be omitted if the measured temperature difference .DELTA.T is less than a minimum temperature difference .DELTA.T min , make no sense below the corrections of the correction factor K, since the measurement accuracy of the temperature sensor 15 is only about 2.5 ° C.
  • the Fig. 9 shows in a diagram the course of the three curves 16 to 18 during a later phase of operation, during which the heater controller requested by the heating power P changes over again.
  • the course of the rotational speed D (t) of the blower 2 is not shown here.
  • the update of the correction factor K is carried out according to predetermined criteria, preferably independently of the operating state of the burner periodically with the frequency f 2 , in the example in a clock of 15 minutes, as described above.
  • the update can also occur when certain events occur or even aperiodic.
  • the correction factor K (P) is continuously updated and stored as described. It is retained even if the evaporator burner is switched off. The next time the evaporator burner starts, the stored correction factor K (P) serves as the output value.
  • the interpolation point values K 1 and K 2 are increased by a predetermined value, for example by 0.02.
  • the correction factor K ie here the interpolation point values K 1 and K 2 , is automatically reset to 0.
  • the burner does not run stably, which manifests itself as considerable fluctuations in the heating power, it is advantageous to make no or a change in the correction factor K which is less than normal.
  • the update of the correction factor K takes place in a fixed clock at predetermined times. If the variation of the heating power from the last time to the new time exceeds a predetermined value, then the correction factor K is not or only partially updated.
  • the fuel pump 13 is, for example, an oscillating piston pump.
  • the amount of fuel delivered is proportional to the operating frequency, the so-called metering F.
  • the factor ⁇ will be checked if necessary and updated if necessary.
  • the updating of the factor ⁇ is preferably carried out when the evaporator burner runs stable at low load P min , because at low load, the dependence of the mentioned process variables of the excess air least and the sensitivity of the mentioned process variables is greatest.

Landscapes

  • 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)
EP08105288.8A 2007-09-12 2008-09-10 Procédé de commande d'un brûleur à évaporation Not-in-force EP2037176B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH01442/07A CH700427B1 (de) 2007-09-12 2007-09-12 Verfahren zum Steuern eines Verdampferbrenners.

Publications (3)

Publication Number Publication Date
EP2037176A2 true EP2037176A2 (fr) 2009-03-18
EP2037176A3 EP2037176A3 (fr) 2017-06-21
EP2037176B1 EP2037176B1 (fr) 2018-07-18

Family

ID=40111614

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08105288.8A Not-in-force EP2037176B1 (fr) 2007-09-12 2008-09-10 Procédé de commande d'un brûleur à évaporation

Country Status (2)

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EP (1) EP2037176B1 (fr)
CH (1) CH700427B1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3182007A1 (fr) * 2015-12-18 2017-06-21 Robert Bosch Gmbh Système d'appareil de chauffage et procédé faisant appel à un système d'appareil de chauffage
CN116370676A (zh) * 2023-03-31 2023-07-04 山东博科消毒设备有限公司 一种过氧化氢汽化装置及方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000012935A1 (fr) 1998-09-01 2000-03-09 Toby Ag Bruleur destine a des combustibles liquides
WO2004109183A1 (fr) 2003-06-11 2004-12-16 Toby Ag Bruleur pour combustibles liquides

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3743205A1 (de) * 1987-12-19 1989-06-29 Schrag Heizungs Lueftungs Klim Brenneinrichtung
DE4323586C2 (de) * 1993-07-14 1998-01-29 Eberspaecher J Gmbh & Co Fahrzeugheizeinrichtung
JP2000018571A (ja) * 1998-07-03 2000-01-18 Sanyo Electric Co Ltd 液体燃料燃焼装置
DE10109438C2 (de) * 2001-02-27 2003-08-14 Webasto Thermosysteme Gmbh Heizgerät mit einer Fördereinrichtung, insbesondere Zusatzheizgerät für ein Fahrzeug

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000012935A1 (fr) 1998-09-01 2000-03-09 Toby Ag Bruleur destine a des combustibles liquides
WO2004109183A1 (fr) 2003-06-11 2004-12-16 Toby Ag Bruleur pour combustibles liquides

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3182007A1 (fr) * 2015-12-18 2017-06-21 Robert Bosch Gmbh Système d'appareil de chauffage et procédé faisant appel à un système d'appareil de chauffage
CN116370676A (zh) * 2023-03-31 2023-07-04 山东博科消毒设备有限公司 一种过氧化氢汽化装置及方法

Also Published As

Publication number Publication date
EP2037176A3 (fr) 2017-06-21
CH700427B1 (de) 2010-08-31
EP2037176B1 (fr) 2018-07-18

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