EP0034786B1 - Verfahren zum Betrieb einer Heizkesselanlage und dafür geeignete Vorrichtung - Google Patents

Verfahren zum Betrieb einer Heizkesselanlage und dafür geeignete Vorrichtung Download PDF

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Publication number
EP0034786B1
EP0034786B1 EP81101082A EP81101082A EP0034786B1 EP 0034786 B1 EP0034786 B1 EP 0034786B1 EP 81101082 A EP81101082 A EP 81101082A EP 81101082 A EP81101082 A EP 81101082A EP 0034786 B1 EP0034786 B1 EP 0034786B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
burner
boiler
combustion chamber
output
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.)
Expired
Application number
EP81101082A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0034786A1 (de
Inventor
Alfred Dr. Michel
Hana Dipl.-Ing. Kostka
Hermann-Otto Dipl.-Ing. Berg
Louis Gosteli
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Priority to AT81101082T priority Critical patent/ATE11450T1/de
Publication of EP0034786A1 publication Critical patent/EP0034786A1/de
Application granted granted Critical
Publication of EP0034786B1 publication Critical patent/EP0034786B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/0027—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using fluid fuel
    • F24H1/0045—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using fluid fuel with catalytic combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/285—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with the fire tubes arranged alongside the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/235—Temperature of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/355—Control of heat-generating means in heaters
    • F24H15/36—Control of heat-generating means in heaters of burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
    • F24H9/2035—Arrangement or mounting of control or safety devices for water heaters using fluid fuel

Definitions

  • the invention relates to a method for operating a boiler system with a heat exchanger downstream of the combustion chamber, the effective heat exchanger area being adapted to the burner output, and to a corresponding device for operating a boiler system.
  • Oil burners are widely used in conventional boiler systems.
  • Conventional medium-power oil burners atomize the heating oil with the help of a nozzle and burn it when there is excess air to keep soot formation low.
  • the atomizing burner output can be controlled only with great difficulty and only within narrow limits. For this reason, atomizing burners for boiler systems are operated intermittently, so that the average power value corresponds to the heat output requirement.
  • the boiler water and also the gas temperature fluctuate in the combustion chamber, in the heat exchanger, in the exhaust pipe and / or in the chimney, which is very undesirable. Larger fluctuations in the exhaust gas temperature should be avoided, in particular, because considerable losses of energy occur at high temperatures and because at low temperatures there is a risk that the acid dew point will be undershot and there will be signs of corrosion.
  • a flame tube or heating boiler is known from DE-A-2 631 567, which has uncontrolled flue gas tubes and, in addition, one or more regulated flue gas tubes, so-called control tubes, which are connected downstream of the combustion chamber of the burner. All control tubes are always more or less open, and that in all burner load conditions.
  • the control pipes which are equipped with smoke flaps, change the free gas cross-section; in addition, the pressure or the flow rate of the flue gases is also changed. In order to maintain a constant pressure on the flue gas side, a control pressure flap is also available in this boiler.
  • the object of the invention is to design a boiler system of the type mentioned at the outset in such a way that it can be operated continuously, the flue gas temperature of the boiler - even with variable heat output requirements and proportional burner output - maintaining a predetermined value.
  • the heating power requirement for example of a residential building, - like the heating flow temperature - depends approximately linearly on the outside air temperature. This relationship is shown schematically in FIG. 1. From Fig. 1 it can be seen that the power requirement fluctuates approximately between 15 and 100% of the rated burner output (outside air temperature: +15 to -15 ° C). Since in a heat exchanger the transferred heat output is a function of the temperature difference and the heat exchanger area, the effective heat exchanger area is therefore regulated according to a function dependent on the load in the method according to the invention. In this way, the flue gas temperature in the boiler operated with a continuously adjustable burner is kept constant - regardless of the load-proportional burner output. H. the flue gas temperature at the boiler system outlet maintains a specified value within certain limits.
  • the “effective heat exchanger surface” is understood to mean that part of the heat-exchanging surface over which - in a certain operating state - the heat transfer essentially takes place. These are generally surfaces that are in contact with flowing exhaust gas, so they are essentially the so-called secondary heating surfaces.
  • Ver steam burners such as cup burners can be used.
  • a gas burner is used in the method according to the invention for operating the boiler system.
  • a continuously adjustable burner is known for example from DE-B-2 811 273.
  • the gasification burner used in the method according to the invention can advantageously be further developed in such a way that the annular space also surrounds the ignition chamber and the conically widening combustion chamber in an annular manner and extends into the vicinity of the burner plate and that there is a primary air supply nozzle in the Annulus opens (see: DE-A-2 841 105).
  • the side walls of the ignition chamber and the combustion chamber can be made of metal and have a ceramic lining.
  • the ignition chamber can be separated from the combustion chamber by a perforated wall in such a way that the perforated area of the burner plate is larger than the perforated area of the perforated wall.
  • a flame monitoring device directed towards the perforated wall can also be provided on the housing.
  • the well-known gasification burner is based on the principle of two-stage combustion.
  • heating oil is gasified in a catalytic reactor by partial oxidation with air at air ratios between 0.05 and 0.2, preferably around 0.1.
  • the product gas obtained in this way, the so-called fuel gas is then stoichiometrically burnt in the second stage with the remaining air, high firing temperatures being reached.
  • An advantageous device for carrying out the method according to the invention is characterized in that a tube bundle heat exchanger is connected downstream of the combustion chamber of the boiler.
  • a tube bundle heat exchanger is connected downstream of the combustion chamber of the boiler.
  • the necessary adaptation of the effective heat exchanger surface to the variable burner output is carried out by gradually switching on the tube bundle heat exchanger downstream of the combustion chamber, in such a way that the number of open tubes of the heat exchanger is a function that increases monotonously with the burner output.
  • the stoichiometric i.e. H. is operated without substantial excess air, for example at a constant boiler water temperature
  • the number of open heat exchanger tubes is simultaneously proportional to the amount of exhaust gas, since this is directly proportional to the burner output.
  • this also means that when a boiler system according to the invention is operated with a constant boiler water temperature, the exhaust gas at the boiler outlet has not only a constant temperature under all operating conditions, but also a constant flow rate.
  • the change of the heat exchanger surface by switching tube bundle elements on and off can take place in the boiler system according to the invention in such a way that within the individual elements, ie. H. throttle valves are installed in the tubes or at the outlet of the tube bundle (in the individual elements).
  • a step diaphragm must be arranged near the firebox.
  • the heat exchanger surface of the tube bundle heat exchanger is preferably adapted to the burner output by means of a rotary valve arranged at the tube bundle outlet.
  • a servomotor can be provided to actuate the rotary slide valve, but an expansion thermostat at the outlet of the heat exchanger can also be used.
  • the regulation at the outlet of the heat exchanger has the advantage that a relatively cold exhaust gas has to be regulated; this is mechanically easier to do.
  • the tube bundle exit is also more easily accessible.
  • the control of the rotary slide valve or the step orifice plate or the throttle valve depends on the load, ie the burner output.
  • the fuel oil volume flow supplied to the burner can be used for this purpose, for example.
  • air ratio A 1.0
  • the air mass flow supplied to the burner can also be obtained be attracted.
  • a thermal sensor can also be attached in the exhaust pipe.
  • This thermal sensor can - in addition - be used to control rotary valves, etc.
  • temperature deviations in the exhaust gas can be taken into account, which result, for example, from a change in the calorific value of the primary fuel used.
  • the minimum burner output (during the transition period) is around 10 to 15% of the maximum output.
  • a 15 kW burner for example, must therefore be able to be reduced to approximately 2 kW.
  • the burner control range and the permissible flue gas temperature the following would result - without the measures according to the invention: If the boiler were designed for the lower limits of the flue gas temperature and the burner output, the flue gas temperature would rise sharply at maximum burner output and the system efficiency would decrease as a result.
  • the disadvantages mentioned are not present in the boiler system according to the invention, because here - through the measures explained above - a constant flue gas temperature is guaranteed.
  • the variable part of the heat exchanger corresponds to the control range and the unchangeable part to the lower output limit of the burner.
  • the - unchangeable - heat exchanger surface of the combustion chamber including the heat exchanger surface of an always open tube of the shell-and-tube heat exchanger, advantageously corresponds to approximately 10% of the maximum burner output, while the surface of the heat exchanger connected downstream of the combustion chamber is regulated in such a way that the exhaust gas temperature remains constant when the burner output increases from 10 to 100%.
  • FIG. 1 shows the boiler water temperature and the heating output of a boiler system as a function of the outside air temperature.
  • FIG. 2 shows schematically a longitudinal section through an embodiment of the boiler system according to the invention and in FIG. 3 the section III-III through the embodiment according to FIG. 2.
  • the boiler system 10 is provided with a feed pipe 11 and a return pipe 12 for the hot water.
  • a controllable burner 15 projects into the combustion chamber 13, which is surrounded by a shell-and-tube heat exchanger 14.
  • the furnace 13 of the boiler system 10 is cylindrical, and the shell-and-tube heat exchanger 14 is arranged coaxially therewith.
  • the combustion chamber has an inside diameter of 195 mm and a length of 350 mm.
  • a fixed exhaust gas barrier 16 and a rotary valve 17 are arranged at the outlet of the tube bundle heat exchanger 14.
  • the rotary slide valve 17 is actuated by a servomotor 18 as a function of the burner output and successively releases the openings of the tubes 19 of the tube bundle heat exchanger 14.
  • a servomotor 18 As a function of the burner output and successively releases the openings of the tubes 19 of the tube bundle heat exchanger 14.
  • the range of rotation of the rotary valve 17 is set so that the combustion chamber 13 is always connected to the exhaust gas line 20 via at least one tube 19 of the tube bundle heat exchanger 14, i. H. one of the tubes 19 is always open.
  • a boiler system that can be continuously regulated between approx. 2 and 12 kW heating output has, for example, 29 exhaust pipes that can be switched on successively. With 4, 6, 8 and 10 kW thermal output, the following exhaust gas composition results: soot number 0.13.5% C0 2 , 0.5% CO and 0.3 to 0.7% O z .
  • a constant exhaust gas temperature of approx. 100 ° C can be achieved here, as shown in FIG. 4, by switching on exhaust pipes from 5 kW in proportion to the load.
  • the exhaust gas temperature is therefore kept at a value of approx. 100 ° C in order to maintain a sufficient distance from the acid dew point, which is approx. 85 ° C (use of a heating oil with a content of 0.3 to 0.55% by weight Sulfur).
  • FIG. 4 also shows, for an exhaust gas temperature of 120 ° C.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Air Supply (AREA)
  • Waste-Gas Treatment And Other Accessory Devices For Furnaces (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Control Of Combustion (AREA)
EP81101082A 1980-02-18 1981-02-16 Verfahren zum Betrieb einer Heizkesselanlage und dafür geeignete Vorrichtung Expired EP0034786B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81101082T ATE11450T1 (de) 1980-02-18 1981-02-16 Verfahren zum betrieb einer heizkesselanlage und dafuer geeignete vorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803006048 DE3006048A1 (de) 1980-02-18 1980-02-18 Verfahren zum betrieb einer heizkesselanlage und dafuer geeignete vorrichtung
DE3006048 1980-02-18

Publications (2)

Publication Number Publication Date
EP0034786A1 EP0034786A1 (de) 1981-09-02
EP0034786B1 true EP0034786B1 (de) 1985-01-23

Family

ID=6094920

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81101082A Expired EP0034786B1 (de) 1980-02-18 1981-02-16 Verfahren zum Betrieb einer Heizkesselanlage und dafür geeignete Vorrichtung

Country Status (8)

Country Link
US (1) US4730578A (no)
EP (1) EP0034786B1 (no)
JP (1) JPS56133553A (no)
AT (1) ATE11450T1 (no)
CA (1) CA1174127A (no)
DE (2) DE3006048A1 (no)
DK (1) DK150123C (no)
NO (1) NO149292C (no)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3027802C3 (de) * 1980-07-23 1988-08-18 Buderus Heiztechnik GmbH, 6330 Wetzlar Regelung eines Heizungskessels
DE19819139C2 (de) * 1998-04-29 2003-06-18 Deutsch Zentr Luft & Raumfahrt Heizkessel für eine Feuerungsanlage und einen solchen Heizkessel umfassende Feuerungsanlage
SE520222C2 (sv) 2001-10-15 2003-06-10 Volvo Lastvagnar Ab Ljusströmställare för fordon och metod

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE661629C (de) * 1935-10-17 1938-06-23 Theodor Eickeler Heizkessel mit zwei wahlweise einschaltbaren Steigzuegen
FR1491523A (fr) * 1966-06-30 1967-08-11 Const De Vaux Andigny Atel Procédé pour la chauffe d'une chaudière, et chaudières en comportant application
CH576104A5 (en) * 1974-01-23 1976-05-31 Niggli Florian Flue gas heat utilisation system - has extraction fan and flue closing valve coupled to the burner blower
DE2631567A1 (de) * 1976-07-14 1978-01-19 Gerhard Geng Flammrohr- und heizkessel mit rauchgasseitiger abgastemperaturregelung
DE2811273B1 (de) * 1978-03-15 1979-07-05 Siemens Ag Vergasungsbrenner
DE2800966A1 (de) * 1978-01-11 1979-07-12 Kloeckner Humboldt Deutz Ag Abgaswaermetauscher fuer heizungsanlagen
DE2841105A1 (de) * 1978-09-21 1980-04-10 Siemens Ag Vergasungsbrenner
FR2451551A1 (fr) * 1979-03-13 1980-10-10 Hdg Kessel & App Chaudiere mixte destinee a des combustibles solides et liquides

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2131336A (en) * 1936-08-04 1938-09-27 Sullivan Valve & Engineering Co Direct fired steam mangle
US4151874A (en) * 1977-05-23 1979-05-01 Sumitomo Metal Industries Limited Heat exchanger for flue gas
EP0006163B1 (de) * 1978-06-14 1981-12-23 PPT Pyrolyse- und Prozessanlagentechnik AG Verfahren und Vorrichtungen zur Rauchgasführung in einem Wärmekessel

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE661629C (de) * 1935-10-17 1938-06-23 Theodor Eickeler Heizkessel mit zwei wahlweise einschaltbaren Steigzuegen
FR1491523A (fr) * 1966-06-30 1967-08-11 Const De Vaux Andigny Atel Procédé pour la chauffe d'une chaudière, et chaudières en comportant application
CH576104A5 (en) * 1974-01-23 1976-05-31 Niggli Florian Flue gas heat utilisation system - has extraction fan and flue closing valve coupled to the burner blower
DE2631567A1 (de) * 1976-07-14 1978-01-19 Gerhard Geng Flammrohr- und heizkessel mit rauchgasseitiger abgastemperaturregelung
DE2800966A1 (de) * 1978-01-11 1979-07-12 Kloeckner Humboldt Deutz Ag Abgaswaermetauscher fuer heizungsanlagen
DE2811273B1 (de) * 1978-03-15 1979-07-05 Siemens Ag Vergasungsbrenner
DE2841105A1 (de) * 1978-09-21 1980-04-10 Siemens Ag Vergasungsbrenner
FR2451551A1 (fr) * 1979-03-13 1980-10-10 Hdg Kessel & App Chaudiere mixte destinee a des combustibles solides et liquides

Also Published As

Publication number Publication date
ATE11450T1 (de) 1985-02-15
DE3168413D1 (en) 1985-03-07
US4730578A (en) 1988-03-15
NO810525L (no) 1981-08-19
DE3006048A1 (de) 1981-08-20
NO149292C (no) 1984-03-21
DK67981A (da) 1981-08-19
CA1174127A (en) 1984-09-11
DK150123B (da) 1986-12-08
NO149292B (no) 1983-12-12
JPS56133553A (en) 1981-10-19
EP0034786A1 (de) 1981-09-02
DK150123C (da) 1987-06-15

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