EP4184058A1 - Dispositif de nettoyage amélioré pour installation de chauffage à biomasse - Google Patents

Dispositif de nettoyage amélioré pour installation de chauffage à biomasse Download PDF

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Publication number
EP4184058A1
EP4184058A1 EP22213026.2A EP22213026A EP4184058A1 EP 4184058 A1 EP4184058 A1 EP 4184058A1 EP 22213026 A EP22213026 A EP 22213026A EP 4184058 A1 EP4184058 A1 EP 4184058A1
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EP
European Patent Office
Prior art keywords
cleaning
cleaning device
heating system
crank
combustion chamber
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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.)
Pending
Application number
EP22213026.2A
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German (de)
English (en)
Inventor
Thilo SOMMERAUER
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SL Technik GmbH
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SL Technik GmbH
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Priority to EP22213026.2A priority Critical patent/EP4184058A1/fr
Publication of EP4184058A1 publication Critical patent/EP4184058A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B80/00—Combustion apparatus characterised by means creating a distinct flow path for flue gases or for non-combusted gases given off by the fuel
    • F23B80/04—Combustion apparatus characterised by means creating a distinct flow path for flue gases or for non-combusted gases given off by the fuel by means for guiding the flow of flue gases, e.g. baffles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/01—Pretreatment of the gases prior to electrostatic precipitation
    • B03C3/014—Addition of water; Heat exchange, e.g. by condensation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/017—Combinations of electrostatic separation with other processes, not otherwise provided for
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/34—Constructional details or accessories or operation thereof
    • B03C3/40—Electrode constructions
    • B03C3/41—Ionising-electrodes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/34—Constructional details or accessories or operation thereof
    • B03C3/40—Electrode constructions
    • B03C3/45—Collecting-electrodes
    • B03C3/49—Collecting-electrodes tubular
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/34—Constructional details or accessories or operation thereof
    • B03C3/74—Cleaning the electrodes
    • B03C3/743—Cleaning the electrodes by using friction, e.g. by brushes or sliding elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/34—Constructional details or accessories or operation thereof
    • B03C3/74—Cleaning the electrodes
    • B03C3/76—Cleaning the electrodes by using a mechanical vibrator, e.g. rapping gear ; by using impact
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C3/00—Separating dispersed particles from gases or vapour, e.g. air, by electrostatic effect
    • B03C3/34—Constructional details or accessories or operation thereof
    • B03C3/88—Cleaning-out collected particles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B60/00—Combustion apparatus in which the fuel burns essentially without moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J3/00—Removing solid residues from passages or chambers beyond the fire, e.g. from flues by soot blowers
    • F23J3/02—Cleaning furnace tubes; Cleaning flues or chimneys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L9/00—Passages or apertures for delivering secondary air for completing combustion of fuel 
    • F23L9/02—Passages or apertures for delivering secondary air for completing combustion of fuel  by discharging the air above the fire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24B—DOMESTIC STOVES OR RANGES FOR SOLID FUELS; IMPLEMENTS FOR USE IN CONNECTION WITH STOVES OR RANGES
    • F24B1/00—Stoves or ranges
    • F24B1/02—Closed stoves
    • F24B1/024—Closed stoves for pulverulent fuels
    • 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
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • 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
    • F24H9/0005—Details for water heaters
    • F24H9/0042—Cleaning arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G1/00—Non-rotary, e.g. reciprocated, appliances
    • F28G1/06—Non-rotary, e.g. reciprocated, appliances having coiled wire tools, i.e. basket type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G15/00—Details
    • F28G15/04—Feeding and driving arrangements, e.g. power operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C2201/00—Details of magnetic or electrostatic separation
    • B03C2201/08—Ionising electrode being a rod
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C—MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
    • B03C2201/00—Details of magnetic or electrostatic separation
    • B03C2201/10—Ionising electrode has multiple serrated ends or parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24B—DOMESTIC STOVES OR RANGES FOR SOLID FUELS; IMPLEMENTS FOR USE IN CONNECTION WITH STOVES OR RANGES
    • F24B13/00—Details solely applicable to stoves or ranges burning solid fuels 
    • F24B13/006—Arrangements for cleaning, e.g. soot removal; Ash removal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24B—DOMESTIC STOVES OR RANGES FOR SOLID FUELS; IMPLEMENTS FOR USE IN CONNECTION WITH STOVES OR RANGES
    • F24B5/00—Combustion-air or flue-gas circulation in or around stoves or ranges
    • F24B5/02—Combustion-air or flue-gas circulation in or around stoves or ranges in or around stoves
    • F24B5/021—Combustion-air or flue-gas circulation in or around stoves or ranges in or around stoves combustion-air circulation
    • F24B5/026—Supply of primary and secondary air for combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0024—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion apparatus, e.g. for boilers

Definitions

  • the invention relates to an improved cleaning device for a biomass heating system.
  • Biomass heating systems in particular biomass boilers, in a power range from 20 to 500 kW are known.
  • Biomass can be considered a cheap, domestic, crisis-proof and environmentally friendly fuel.
  • wood chips or pellets as combustible biomass or biogenic solid fuels.
  • the pellets usually consist of wood shavings, sawdust, biomass or other materials that have been compacted into small discs or cylinders approximately 3 to 15 mm in diameter and 5 to 30 mm long.
  • Wood chips also known as wood chips, woodchips, or chips
  • wood chips are wood that has been crushed with cutting tools.
  • Biomass heating systems for fuels in the form of pellets and wood chips essentially have a boiler with a combustion chamber (the combustion chamber) and with an adjoining heat exchange device. Due to the stricter legal regulations in many countries, some biomass heating systems also have a fine dust filter. Other various accessories are regularly available, such as fuel delivery devices, control devices, probes, safety thermostats, pressure switches, exhaust gas recirculation, boiler cleaning and a separate fuel container.
  • a device for supplying fuel, a device for supplying air and an ignition device for the fuel are regularly provided in the combustion chamber.
  • the means for supplying the air normally comprise a low-pressure fan in order to favorably influence the thermodynamic factors of combustion in the combustion chamber.
  • a device for supplying fuel can be provided, for example, with a lateral insert (so-called transverse insert firing). The fuel is pushed into the combustion chamber from the side via a screw or a piston.
  • a furnace grate In the combustion chamber of a fixed-bed furnace, a furnace grate is also usually provided, on which the fuel is essentially supplied and burned continuously.
  • This grate stores the fuel for combustion and has openings, for example slots, which allow the passage of part of the combustion air as primary air to the fuel.
  • the grate can be rigid or movable.
  • the grate When the primary air flows through the grate, the grate is also cooled, which protects the material. In addition, if there is insufficient air supply, slag can form on the grate, whereby the slag can also be detached (e.g. when cleaning the grate) and carried further into the rest of the biomass heating system.
  • furnaces that are to be charged with different fuels with which the present disclosure is particularly concerned, have the inherent problem that the different fuels have different ash melting points, water contents and different combustion behavior and thus variable combustion residues. It is therefore problematic to provide a heating system that is equally well suited for different fuels. Good suitability for different fuels requires regular and efficient cleaning of the biomass heating system.
  • the combustion chamber can also be regularly divided into a primary combustion zone (immediate combustion of the fuel on the grate and in the gas space above it before additional combustion air is supplied) and a secondary combustion zone (post-combustion zone of the flue gas after additional air supply). Drying, pyrolytic decomposition, gasification of the fuel and charcoal combustion take place in the combustion chamber. In order to completely burn the resulting combustible gases, additional combustion air is introduced in one or more stages (secondary air or tertiary air) at the start of the secondary combustion zone.
  • the combustion of the pellets or wood chips essentially has two phases.
  • the fuel is at least partially pyrolytically decomposed and converted into gas by high temperatures and air that can be blown into the combustion chamber.
  • the (partial) part that has been converted into gas is burned, as well as the burning of any remaining solids (e.g. charcoal).
  • the fuel outgasses, and the resulting gas and the charcoal contained therein are also burned.
  • Pyrolysis is the thermal decomposition of a solid substance in the absence of oxygen. Pyrolysis can be divided into primary and secondary pyrolysis.
  • the products of primary pyrolysis are pyrolysis coke and pyrolysis gases, the pyrolysis gases being divided into room temperature condensable and non-condensable gases.
  • the primary pyrolysis takes place at roughly 250-450°C and the secondary pyrolysis at around 450-600°C.
  • the secondary pyrolysis that subsequently occurs is based on the further reaction of the pyrolysis products that were primarily formed.
  • the drying and pyrolysis take place at least largely without the use of air, since volatile CH compounds escape from the particle and therefore no air can reach the particle surface.
  • Gasification can be seen as part of oxidation; the solid, liquid and gaseous products formed during the pyrolytic decomposition are reacted by further exposure to heat. This is done with the addition of a gassing agent such as air, oxygen, water vapor or carbon dioxide.
  • a gassing agent such as air, oxygen, water vapor or carbon dioxide.
  • the lambda value during gasification is greater than zero and less than one. Gasification takes place at around 300 to 850°C or even up to 1,200°C.
  • the complete oxidation with excess air (lambda greater than 1) takes place by adding more air to these processes.
  • the end products of the reaction are essentially carbon dioxide, water vapor and ash. In all phases, the boundaries are not rigid, but fluid.
  • the combustion process can be advantageously regulated by means of a lambda probe provided at the exhaust gas outlet of the boiler.
  • the combustion of biomass produces gaseous or airborne combustion products, the main components of which are carbon, hydrogen and oxygen. These can be divided into emissions from complete oxidation, from incomplete oxidation and substances from trace elements or impurities.
  • the emissions from complete oxidation are essentially carbon dioxide (CO 2 ) and water vapor (H 2 O).
  • the formation of carbon dioxide from the carbon in the biomass is the goal of combustion, as the released energy can be used more fully.
  • the release of carbon dioxide (CO 2 ) is largely proportional to the carbon content of the fuel burned; thus the carbon dioxide is also dependent on the useful energy to be provided. A reduction can essentially only be achieved by improving the efficiency.
  • the boiler further usually has a radiant part, which is integrated into the combustion chamber, and a convection part (the heat exchanger connected thereto).
  • the exhaust gas from the combustion in the combustion chamber is fed to the heat exchanger so that the hot combustion gases flow through the heat exchanger in order to To transfer heat to a heat exchange medium, which is typically water at about 80°C (usually between 70°C and 110°C). During this cooling process in particular, combustion residues can get stuck in the pipes of the heat exchanger and also adhere very firmly.
  • a heat exchange medium typically water at about 80°C (usually between 70°C and 110°C).
  • combustion residues can adhere to the walls or other parts of the boiler, depending on the temperature condition or also, for example, in the event of condensation and also in an (optional) electrostatic precipitator.
  • a particular problem is that the adhesion of the combustion residues can be very strong or permanent, which means that cleaning the boiler (especially when cleaning it by hand) is quite difficult.
  • Practice shows that the combustion residues can stick or cake, especially in the heat exchanger and in the (optional) electrostatic precipitator, which makes cleaning them even more difficult.
  • furnaces that are to be charged with different fuels have the inherent problem that the different fuels have different ash melting points, water contents and different combustion behavior.
  • heating systems with fuel-flexible charging have the problem of very variable - in practice hardly predictable - formation of combustion residues with different chemical and physical properties.
  • cleaning of the biomass heating system must also be able to cope with these different combustion residues.
  • the other problems with conventional biomass heating systems are that the gaseous or solid emissions are too high, that the efficiency is too low and that the dust emissions are too high.
  • Another problem is the varying quality of the fuel, due to the varying water content and the lumpiness of the fuel, which makes it difficult to burn the fuel evenly with low emissions.
  • biomass heating systems which are intended to be suitable for different types of biological or biogenic fuel
  • the varying quality and consistency of the fuel makes it difficult to maintain consistently high efficiency of the biomass heating system. There is a need for optimization in this regard.
  • a disadvantage of traditional pellet biomass heating systems can be that pellets falling into the combustion chamber can roll off the grid or grate, slide off, or land next to the grate and end up in an area of the combustion chamber where the temperature is lower or where the air supply is poor, or they can even fall into the bottom chamber of the boiler or the ash chute. Pellets that are not left on the grid or grate burn incompletely, causing poor efficiency, excessive ash and a certain amount of unburned pollutant particles, which in turn pollute the biomass heating system. This applies to pellets as well as wood chips.
  • the EP 1 830 130 A2 As the prior art relating to a cleaning device for a boiler is the EP 1 830 130 A2 known.
  • a safety device which, when the filling door is open or closed and the flue gas flap is open and locked, generates a signal and possibly displays it or releases the locking of the open flue gas flap when the filling door is closed or while the filling door is being closed.
  • the safety device is in particular a spring-loaded rocker arm, which acts as a sensor for an open or closed filling door and as a switching element for operating an operating lever used for the flue gas damper. If necessary, the actuating lever can also actuate a heat exchanger cleaning device at the same time, which is coupled to the flue gas damper.
  • This cleaning device has the disadvantages that it has to be operated manually and that the movement of the heat exchanger cleaning device by operating the operating lever results in an inefficient mechanical cleaning process which has problems in removing the combustion residues from the heat exchanger.
  • Biomass heating systems for pellets or wood chips with cleaning devices of the prior art have the following further disadvantages and problems.
  • the volume of the cleaning process is often quite considerable, which is undesirable, for example, in the case of biomass heating systems for residential buildings.
  • the cleaning is inefficient and requires the cleaning process to be carried out frequently and/or over a longer period of time in order to achieve an adequate cleaning effect.
  • the cleaning is incomplete. Combustion residues remain in the biomass heating system. This applies in particular to the gas-carrying parts of the system, which are not directly touched or caught by the mechanical cleaning.
  • the cleaning devices are mechanically complex. For example, these require a number of different drives and mechanisms provided separately from one another for cleaning the different parts of the system. For example, electrostatic precipitators and heat exchangers are usually cleaned using different mechanisms.
  • the hybrid technology should enable the use of both pellets and wood chips with a water content of between 8 and 35 percent by weight.
  • Gaseous emissions that are as low as possible should be achieved.
  • Very low dust emissions of less than 15 mg/Nm 3 without and less than 5 mg/Nm 3 with electrostatic precipitator operation are aimed for.
  • the task mentioned above or the potential individual problems can also relate to individual partial aspects of the overall system, for example to the combustion chamber, the heat exchanger or the electrical filter device.
  • a cleaning device for a biomass heating system for firing fuel in the form of pellets and/or wood chips having the following: a drive unit for driving the cleaning device, a crank element, which is coupled to the drive unit via a freewheel, the drive unit being able to drive the crank element in one direction of rotation, a thrust element, which - Is provided to be movable and which is coupled to the crank element; at least one cleaning shaft operatively coupled to the thrust member, at least one cleaning element disposed operatively connected to the cleaning shaft; wherein the cleaning device is set up in such a way that when the crank element rotates in the direction of rotation, the thrust member is displaced in a thrust direction by the drive unit; and after a predetermined crank rotational position of the crank element has been exceeded, the thrust member is displaced in an impulse direction which is opposite to the thrust direction.
  • a biomass heating system for firing fuel in the form of pellets and/or wood chips having the following: a boiler with a burner, a heat exchanger with a plurality of boiler tubes, a cleaning device, which has the following: a drive unit for driving the cleaning device, a crank element which is coupled to the drive unit via a freewheel, the drive unit rotating the crank element in one direction can drive, a pushing member which is reciprocably provided and which is coupled to the crank member; at least one cleaning shaft operatively coupled to the thrust member, at least one cleaning element disposed operatively connected to the cleaning shaft; wherein the cleaning device is set up in such a way that when the crank element rotates in the direction of rotation, the thrust member is displaced in a thrust direction by the drive unit; and the thrust member, after exceeding a predetermined Crank rotation position of the crank member, is shifted in an impulse direction opposite to the thrust direction.
  • a cleaning device or a biomass heating system is provided, the cleaning device (9) being set up in such a way that the movement of the thrust member in the direction of the impulse is not effected by the drive unit.
  • a cleaning device or a biomass heating system is provided, the cleaning device (9) being set up in such a way that the movement of the thrust member in the direction of the impulse is caused by a torque of the cleaning shaft.
  • a cleaning device or a biomass heating system wherein the at least one cleaning element is raised by the rotation of the crank element until the predetermined crank rotary position is reached, and the at least one cleaning element after the predetermined crank rotary position has been exceeded due to the weight of the accelerates at least one cleaning element o or suddenly falls down.
  • a cleaning device or a biomass heating system is provided, with the cleaning device being set up in such a way that the movement of the pushing member in the pushing direction takes place at least approximately uniformly.
  • a cleaning device or a biomass heating system is provided, with the cleaning device being set up in such a way that the movement of the thrust member is accelerated in the pulse direction.
  • a cleaning device or a biomass heating system is provided, with the thrust member having an opening for a crank extension of the crank element.
  • a cleaning device or a biomass heating system is provided, with the thrust member having at least one elongate guide hole for receiving at least one guide pin for movably guiding the thrust member.
  • a cleaning device or a biomass heating system is provided, with the thrust member being arranged so that it can be moved back and forth in a straight line.
  • a cleaning device or a biomass heating system wherein the at least one cleaning shaft has a lever with a lever pin on an end of the lever that is distal in relation to the cleaning shaft; and the thrust member has at least one elongated fulcrum pin hole for movably receiving the fulcrum pin.
  • a cleaning device or a biomass heating system is provided, with the at least one cleaning element being at least one turbulator, preferably a spiral turbulator and/or a belt turbulator, which is or are provided in at least one boiler tube of the heat exchanger .
  • a cleaning device or a biomass heating system is provided, the cleaning device being set up in such a way that the freewheel transmits the torque of the motor in the direction of rotation of the crank element; and the freewheel releases further rotation of the crank element in the direction of rotation when the predetermined crank rotational position of the crank element is exceeded.
  • a cleaning device or a biomass heating system is provided, with the thrust member having a stop as the end stop for the movement in the pulse direction.
  • a cleaning device or a biomass heating system is provided, with an opening of the thrust member being provided for receiving a roller of the crank extension.
  • the opening can have a diameter in one direction of the opening which corresponds approximately to the crank radius plus the radius of the roller (or the crank extension); and the opening may have a diameter in another direction perpendicular to the one direction that is less than about the crank radius plus the radius of the pulley (or crank extension).
  • a cleaning device or a biomass heating system is provided, with the opening of the thrust member having a step that is exceeded by the roller when the predetermined crank rotary position is reached.
  • a cleaning device or a biomass heating system is provided, this further comprising: a damping element, preferably a spring, which is arranged such that the damping element dampens the movement of the thrust member in the thrust direction.
  • a cleaning device or a biomass heating system wherein: a contraction and expansion direction of the damping element is provided at least approximately parallel to the direction of the back and forth movement of the damping element.
  • a cleaning device or a biomass heating system is provided, with the thrust member being provided in the form of a plate and/or wherein one end of the at least one cleaning shaft serves as a guide pin for receiving in an elongate guide hole.
  • a cleaning device or a biomass heating system comprising: an electrostatic filter device with a spray electrode and a cleaning cage as a counter-electrode, the cleaning element being a striking lever; and wherein the impact lever is operatively connected to the cleaning shaft and is arranged in such a way that the impact lever strikes the discharge electrode for cleaning when the cleaning shaft rotates abruptly.
  • a cleaning device or a biomass heating system is provided, with a sensor, for example an inductive position switch, being provided for detecting the position or the end position of the thrust member.
  • a cleaning device or a biomass heating system is provided, with an ash discharge screw of the biomass heating system also being driven by the drive unit.
  • biomass heating system can be further improved in synergy with the optimized cleaning device.
  • a biomass heating system for firing fuel in the form of pellets and/or wood chips comprising the following: a boiler with a combustion device, a heat exchanger with a plurality of boiler tubes, the A combustor comprising: a combustor having a rotary grate, having a primary combustion zone, and having a secondary combustion zone; the primary combustion zone being encompassed by a plurality of combustion chamber bricks laterally and by the rotary grate from below; a plurality of secondary air nozzles being provided in the combustor bricks; the primary combustion zone and the secondary combustion zone being separated at the level of the secondary air nozzles; wherein the secondary combustion zone of the combustor is fluidly connected to an inlet of the heat exchanger.
  • a biomass heating system is provided, with the secondary air nozzles being arranged in such a way that in the secondary combustion zone of the combustion chamber, turbulent flows of a flue gas-air mixture of secondary air and combustion air are created around a vertical central axis, with the turbulent flows to improve the mixing of the flue gas -lead air mixture.
  • a biomass heating system is provided, with the secondary air nozzles in the combustion chamber bricks each being designed as a cylindrical or truncated cone-shaped opening in the combustion chamber bricks with a circular or elliptical cross section, the smallest diameter of the respective opening being smaller than its maximum length.
  • a biomass heating system is provided, the combustion device with the combustion chamber being set up in such a way that the turbulent flows form spiral-shaped rotational flows after exiting the combustion chamber nozzle, which reach up to a combustion chamber ceiling of the combustion chamber.
  • a biomass heating system is provided, with the secondary air nozzles being arranged at least approximately at the same height in the combustion chamber; and the secondary air nozzles are arranged with their center axis as such and/or (depending on the type of nozzle) are aligned in such a way that the secondary air is introduced acentrically to a center of symmetry of the combustion chamber.
  • a biomass heating system is provided, with the number of secondary air nozzles being between 8 and 14; and/or the secondary air nozzles have a minimum length of at least 50 mm with an inner diameter of 20 to 35 mm.
  • a biomass heating system is provided the combustion chamber in the secondary combustion zone has a combustion chamber slope which reduces the cross section of the secondary combustion zone in the direction of the inlet of the heat exchanger.
  • a biomass heating system is provided, with the combustion chamber in the secondary combustion zone having a combustion chamber cover which is provided inclined upwards in the direction of the inlet of the heat exchanger and which reduces the cross section of the combustion chamber in the direction of the inlet.
  • a biomass heating system is provided, with the combustion chamber slope and the inclined combustion chamber ceiling forming a funnel, the smaller end of which opens into the inlet of the heat exchanger.
  • a biomass heating system is provided, with the primary combustion zone and at least part of the secondary combustion zone having an oval horizontal cross section; and/or the secondary air nozzles are arranged in such a way that they introduce the secondary air tangentially into the combustion chamber.
  • a biomass heating system is provided, with the average flow speed of the secondary air in the secondary air nozzles being at least 8 m/s, preferably at least 10 m/s.
  • a biomass heating system with the combustion chamber bricks having a modular structure; and any two semi-circular combustor bricks form a closed ring to form the primary combustion zone and/or part of the secondary combustion zone; and at least two rings of bricks are stacked one on top of the other.
  • a biomass heating system with the heat exchanger having spiral turbulators arranged in the boiler tubes, which extend over the entire length of the boiler tubes; and the heat exchanger includes strip turbulators located in the boiler tubes and extending at least half the length of the boiler tubes.
  • a biomass heating system for firing fuel in the form of pellets and/or wood chips which has the following: a boiler with a combustion device, a heat exchanger with a plurality of boiler tubes, preferably arranged in a bundle-like manner, the combustor comprising: a combustor having a rotary grate and having a primary combustion zone and a secondary combustion zone, preferably provided above the primary combustion zone; the primary combustion zone being encompassed by a plurality of combustion chamber bricks laterally and by the rotary grate from below; wherein secondary combustion zone includes a combustor nozzle or burn-through hole; wherein the secondary combustion zone of the combustor is fluidly connected to an inlet of the heat exchanger; wherein the primary combustion zone has an oval horizontal cross-section.
  • boiler tubes arranged in a bundle-like manner there can be a plurality of boiler tubes which are arranged parallel to one another and have at least largely the same length.
  • the inlet openings and the outlet openings of all boiler tubes can each be arranged in a common plane; ie the inlet openings and the outlet openings of all boiler tubes are at the same level.
  • horizontal can denote a level orientation of an axis or a cross section, assuming that the boiler is also set up horizontally, with which, for example, the ground level can be the reference.
  • horizontal as used herein means “parallel” to the base plane of vessel 11 as commonly defined. Further alternatively, in particular if there is no reference plane, “horizontal” can be understood merely as “parallel” to the combustion plane of the grate.
  • the primary combustion zone can have an oval cross-section.
  • the oval horizontal cross-section has no dead corners and thus has an improved air flow and the possibility of a largely unimpeded turbulent flow. Consequently, the biomass heating system has improved efficiency and lower emissions.
  • the oval cross-section is well adapted to the type of fuel distribution when it is fed in from the side and the resulting geometry of the fuel bed on the grate.
  • An ideally "round" cross section is also possible, but not so well adapted to the geometry of the fuel distribution and also to the flow technology of the turbulent flow, with the asymmetry of the oval compared to the "ideally" circular cross-sectional shape of the combustion chamber improving the formation of a turbulent flow in the combustion chamber allows.
  • a biomass heating system is provided, with the horizontal cross section of the primary combustion zone being provided at least approximately the same over a height of at least 100 mm. This also serves to ensure the unhindered development of the flow profiles in the combustion chamber.
  • a biomass heating system is provided, with the combustion chamber in the secondary combustion zone having a combustion chamber slope which narrows the cross section of the secondary combustion zone in the direction of the inlet or inlet of the heat exchanger.
  • a biomass heating system having a first rotary grate element, a second rotary grate element and a third rotary grate element, each of which rotates about a horizontally arranged bearing axis by at least 90 degrees, preferably at least 160 degrees, even more preferably by at least 170 degrees , are rotatably arranged; wherein the rotary grate elements form a combustion surface for the fuel; wherein the rotary grate elements have openings for the air for combustion, wherein the first rotary grate element and the third rotary grate element are identical in their combustion surface.
  • the openings in the rotary grate elements are preferably designed in the form of slots and in a regular pattern in order to ensure a uniform flow of air through the fuel bed.
  • a biomass heating system is provided, with the second rotary grate element being arranged in a form-fitting manner between the first rotary grate element and the third rotary grate element and having grate lips which are arranged in such a way that, when all three rotary grate elements are in the horizontal position, they at least largely form a seal on the first rotary grate element and the third rotary grate element.
  • a biomass heating system with the rotary grate also having a rotary grate mechanism that is configured in such a way that it can rotate the third rotary grate element independently of the first rotary grate element and the second rotary grate element, and that this rotates the first rotary grate element and the second rotary grate element together but can rotate independently of the third rotary grate element.
  • a biomass heating system is provided, with the combustion surface of the rotary grate elements being configured as an essentially oval or elliptical combustion surface.
  • a biomass heating system wherein the rotary grate elements have mutually complementary and curved sides, wherein preferably the second rotary grate element has concave sides towards the adjacent first and third rotary grate elements respectively, and preferably the first and third rotary grate elements each have a convex side towards the second rotary grate element.
  • a biomass heating system with the combustion chamber bricks having a modular structure; and every two semi-circular combustor bricks form a closed ring to form the primary combustion zone; and at least two rings of bricks are stacked one on top of the other.
  • a biomass heating system with the heat exchanger having spiral turbulators arranged in the boiler tubes, which extend over the entire length of the boiler tubes; and the heat exchanger includes strip turbulators located in the boiler tubes and extending at least half the length of the boiler tubes.
  • the band turbulators can preferably be arranged in or inside the spiral turbulators.
  • the band turbulators can be integrated into the spiral turbulators.
  • the band turbulators can preferably extend over a length of 30 to 70% of the length of the spiral turbulators.
  • a biomass heating system is provided, with the heat exchanger having between 18 and 24 boiler tubes, each with a diameter of 70 to 85 mm and a wall thickness of 3 to 4 mm.
  • a biomass heating system having an integrated electrostatic filter device, which has a spray electrode and a precipitation electrode surrounding the spray electrode and a cage or a cage-like cleaning device; wherein the boiler further comprises a mechanically operable cleaning device with a hammer with a stop head; wherein the cleaning device is set up in such a way that it can hit the end of the (spray) electrode with the stop head, so that a shock wave is generated through the electrode and/or a transverse vibration of the (spray) electrode in order to clean the electrode of impurities.
  • a steel is provided as the material for the electrode, which can be caused to oscillate (longitudinally and/or transversely and/or shock wave) by the stop head.
  • Spring steel and/or chromium steel can be used for this purpose.
  • the material of the spring steel can preferably be an austenitic chromium-nickel steel, for example 1.4310.
  • the spring steel can be cambered.
  • the cage-shaped cleaning device can be further moved back and forth along the wall of the electrostatic filter device for cleaning the collecting electrode.
  • a biomass heating system is provided, with a cleaning device integrated in the boiler in the cold area being provided, which is configured in such a way that it can clean the boiler tubes of the heat exchanger by moving turbulators provided in the boiler tubes up and down.
  • the up and down movement can also be understood as the reciprocating movement of the turbulators in the boiler tubes in the longitudinal direction of the boiler tubes.
  • a biomass heating system with a fire bed height measuring mechanism being arranged in the combustion chamber above the rotary grate; wherein the firebed height measurement mechanism comprises a fuel level flap mounted on a pivot and having a major surface; wherein a surface parallel of the main surface of the fuel level flap is provided at an angle to a central axis of the axis of rotation, the angle preferably being greater than 20 degrees.
  • a combustion chamber slope of a secondary combustion zone of a combustion chamber with the features and properties mentioned herein is disclosed, which is (only) suitable for a biomass heating system.
  • a combustion chamber incline for a secondary combustion zone of a combustion chamber of a biomass heating system with the features and properties mentioned herein is disclosed.
  • a rotary grate for a combustion chamber of a biomass heating system with its features and properties mentioned herein is disclosed.
  • an integrated electrostatic filter device for a biomass heating system with the features and properties mentioned herein is disclosed.
  • a ember bed height measuring mechanism for a biomass heating system with the features and properties mentioned herein is disclosed.
  • a fuel level flap for a biomass heating system with the features and properties mentioned herein is also disclosed.
  • an expression such as “A or B”, “at least one of “A or/and B” or “one or more of A or/and B” can include any possible combination of features listed together.
  • Expressions such as “first “, “secondary”, “primary” or “secondary” used herein represent and do not limit various elements regardless of their order and/or importance.
  • an element e.g., a first element
  • another element e.g., a second element
  • the element may be directly connected to the other element become or are connected to the other element via another element (e.g. a third element).
  • a phrase “configured for” (or “configured for”) as used in the present disclosure may be replaced with “suitable for,” “suitable for,” “adapted for,” “made for,” “capable of,” or “designed for.” depending on what is technically possible.
  • a phrase “device configured to” or “set up to” may mean that the device can operate in conjunction with another device or component, or perform a corresponding function.
  • FIG. 1 shows a three-dimensional overview of the biomass heating system 1 according to an exemplary embodiment of the invention.
  • the arrow V in the figures indicates the front view of the plant 1
  • the arrow S in the figures indicates the side view of the plant 1.
  • the biomass heating system 1 has a boiler 11 which is mounted on a base 12 of the boiler.
  • the boiler 11 has a boiler housing 13, for example made of sheet steel.
  • a combustion device 2 (not shown), which can be reached via a first maintenance opening with a closure 21 .
  • a rotary mechanism mount 22 for a rotary grate 25 (not shown) supports a rotary mechanism 23 with which drive forces can be transmitted to bearing axles 81 of the rotary grate 25 .
  • a heat exchanger 3 (not shown), which can be reached from above via a second maintenance opening with a closure 31 .
  • an optional filter assembly 4 (not shown) having an electrode 44 (not shown) suspended by an insulating electrode support 43 and powered by an electrode supply line 42 .
  • the exhaust gas from the biomass heating system 1 is discharged via an exhaust gas outlet 41 which is arranged downstream of the filter device 4 in terms of flow.
  • a fan can be provided here.
  • a recirculation device 5 is provided downstream of the boiler 11, which recirculates part of the exhaust gas via recirculation channels 51, 53 and 54 and flaps 52 for cooling the combustion process and reuse in the combustion process.
  • the biomass heating system 1 has a fuel supply 6, with which the fuel is conveyed in a controlled manner to the combustion device 2 in the primary combustion zone 26 from the side onto the rotary grate 25.
  • the fuel supply 6 has a cell wheel sluice 61 with a fuel supply opening 65, the cell wheel sluice 61 having a drive motor 66 with control electronics.
  • An axle 62 driven by the drive motor 66 drives a transmission mechanism 63 which can drive a fuel feed screw 67 (not shown) so that the fuel in a fuel feed channel 64 is fed to the combustion device 2 .
  • an ash removal device 7 which has an ash discharge screw 71 in an ash discharge channel which is operated by a drive unit 72 .
  • FIG 2 now shows a cross-sectional view through the biomass heating system 1 of FIG 1 , which was taken along a section line SL1 and which is shown viewed from the side S.
  • a section line SL1 which has the same cut as 2 represents, for the sake of clarity, the flows of the flue gas, and fluidic cross-sections are shown schematically.
  • individual areas compared to the 2 are shown grayed out. This is only for clarity 3 and the visibility of the flow arrows S5, S6 and S7.
  • the boiler 11 is mounted on the boiler base 12 and has a multi-walled boiler housing 13 in which water or another fluid heat exchange medium can circulate.
  • a water circulation device 14 with a pump, valves, lines, etc. is provided for the supply and removal of the heat exchange medium.
  • the combustion device 2 has a combustion chamber 24 in which the combustion process of the fuel takes place in the core.
  • the combustion chamber 24 has a multi-part rotary grate 25 on which the fuel bed 28 rests.
  • the multi-part rotary grate 25 is rotatably mounted by means of a plurality of bearing axles 81 .
  • the primary combustion zone 26 of the combustor 24 is encompassed by (a plurality of) combustor brick(s) 29 , whereby the combustor bricks 29 define the geometry of the primary combustion zone 26 .
  • the cross-section of the primary combustion zone 26 (for example) along the horizontal section line A1 is substantially oval (for example 380mm +/- 60mm x 320mm +/- 60mm; it should be noted that some of the above size combinations may also result in a circular cross-section).
  • the arrow S1 shows the flow from the secondary air nozzle 291 schematically, this flow (this is shown purely schematically) having a twist induced by the secondary air nozzles 291 in order to improve the mixing of the flue gas.
  • the secondary air nozzles 291 are designed in such a way that they introduce the secondary air (preheated by the combustion chamber bricks 29) tangentially into the combustion chamber 24 with its oval cross section there. This creates a flow S1 with vortices or twists, which runs roughly spirally or helically upwards. In other words, a spiral flow running upwards and rotating about a vertical axis is formed.
  • the combustion chamber bricks 29 form the inner lining of the primary combustion zone 26, store heat and are directly exposed to the fire.
  • the combustion chamber stones 29 thus also protect the other material of the combustion chamber 24 , for example cast iron, from the direct effect of the flames in the combustion chamber 24 .
  • the combustion chamber stones 29 are preferably adapted to the shape of the grate 25 .
  • the combustion chamber bricks 29 also have secondary air or recirculation nozzles 291 on, which recirculate the flue gas in the primary combustion zone 26 for re-participation in the combustion process and in particular for cooling as required.
  • the secondary air nozzles 291 are not aligned with the center of the primary combustion zone 26, but are aligned off-centre in order to cause a swirl in the flow in the primary combustion zone 26 (ie, a swirling and turbulent flow).
  • the combustion chamber bricks 29 will be explained in more detail later.
  • Insulation 311 is provided at the boiler tube entrance.
  • the oval cross-sectional shape of the primary combustion zone 26 (and the nozzle) and the length and position of the secondary air nozzles 291 favor the formation and maintenance of a turbulent flow, preferably up to the ceiling of the combustion chamber 24.
  • a secondary combustion zone 27 adjoins the primary combustion zone 26 of the combustion chamber 26, either at the height of the combustion chamber nozzles 291 (from a functional or combustion technology point of view) or at the height of the combustion chamber nozzle 203 (from a purely structural or constructional point of view) and defines the radiant part of the combustion chamber 26.
  • the flue gas produced during combustion releases its thermal energy mainly through thermal radiation, in particular to the heat exchange medium, which is located in the two left-hand chambers for the heat exchange medium 38 .
  • the corresponding flue gas flows are in 3 indicated purely by way of example by the arrows S2 and S3.
  • These turbulent flows may also contain slight backflows or other turbulences, which are not represented by the purely schematic arrows S2 and S3.
  • the basic principle of the development of the flow in the combustion chamber 24 is clear and can be calculated by a person skilled in the art based on the arrows S2 and S3.
  • the oval combustion chamber geometry 24 in particular contributes to the fact that the turbulent flow can develop undisturbed or optimally.
  • candle-flame-shaped rotary flows S2 appear, which are advantageous can reach up to the combustion chamber ceiling 204, so that the available space in the combustion chamber 24 is better utilized.
  • the turbulent flows are concentrated in the center of the combustion chamber A2 and make ideal use of the volume of the secondary combustion zone 27 .
  • the constriction which represents the combustion chamber nozzle 203 for the turbulent flows, reduces the rotational flows, with which turbulences are generated to improve the mixing of the air/flue gas mixture. Cross-mixing therefore takes place through the constriction or constriction through the combustion chamber nozzle 203 .
  • the rotational momentum of the flows is at least partially maintained above the combustion chamber nozzle 203, which maintains the propagation of these flows up to the combustion chamber ceiling 204.
  • the secondary air nozzles 291 are integrated into the elliptical or oval cross-section of the combustion chamber 24 in such a way that, due to their length and their orientation, they induce turbulent flows which cause the flue gas/secondary air mixture to rotate and thereby (again in combination with the combustion chamber nozzle 203 positioned above improved) enable complete combustion with minimal excess air and thus maximum efficiency.
  • the secondary air supply is designed in such a way that it cools the hot combustion chamber bricks 29 by flowing around them and the secondary air itself is preheated in return, whereby the combustion rate of the flue gases is accelerated and the complete combustion even at extreme partial load (e.g. 30% the nominal load) is ensured.
  • the first maintenance opening 21 is insulated with an insulating material such as Vermiculite TM .
  • the present secondary combustion zone 27 is set up in such a way that burnout of the flue gas is ensured.
  • the special geometric design of the secondary combustion zone 27 will be explained in more detail later.
  • the flue gas flows into the heat exchange device 3, which is a bundle of parallel provided Boiler tubes 32 has.
  • the flue gas now flows downwards in the boiler tubes 32, as in 3 indicated by the arrows S4.
  • This part of the flow can also be referred to as the convection part, since the heat dissipation of the flue gas takes place essentially on the boiler tube walls via forced convection. Due to the temperature gradients in the heat exchanger medium, for example in the water, caused in the boiler 11, a natural convection of the water occurs, which promotes thorough mixing of the boiler water.
  • the outlet of the boiler tubes 32 opens into the turning chamber 35 via the turning chamber entry 34 or inlet. If the filter device 4 is not provided, the flue gas is discharged upwards again in the boiler 11 . The other case of the optional filter device 4 is in the 2 and 3 shown. In the process, the flue gas is fed back up into the filter device 4 after the turning chamber 35 (cf. arrows S5), which in the present example is an electrostatic filter device 4. Flow screens can be provided at the inlet 44 of the filter device 4, which even out the inflow of the flue gas into the filter.
  • Electrostatic dust filters also known as electrostatic precipitators, are devices for separating particles from gases that are based on the electrostatic principle. These filter devices are used in particular for the electrical cleaning of exhaust gases.
  • electrostatic precipitators dust particles are electrically charged by a corona discharge of a spray electrode and drawn to the oppositely charged electrode (collecting electrode).
  • the corona discharge takes place on a suitable, charged high-voltage electrode (also known as a discharge electrode) inside the electrostatic precipitator.
  • the electrode is preferably designed with protruding tips and possibly sharp edges, because the density of the field lines and thus also the electric field strength is greatest there and the corona discharge is thus favored.
  • the opposite electrode precipitation electrode usually consists of a grounded exhaust pipe section that is mounted around the electrode.
  • the degree of separation of an electrostatic precipitator depends in particular on the dwell time of the exhaust gases in the filter system and the voltage between the spray and separation electrodes.
  • the rectified high voltage required for this is provided by a high-voltage generating device (not shown).
  • the high-voltage generation system and the holder for the electrode must be protected from dust and dirt in order to avoid unwanted leakage currents and to extend the service life of system 1.
  • a rod-shaped electrode 45 (which is preferably designed like an elongated, plate-shaped steel spring, cf. 11 ) held approximately centrally in an approximately chimney-shaped interior of the filter device 4.
  • the electrode 45 consists at least largely of high-quality spring steel or chromium steel and is held by an electrode holder 43 via a high-voltage insulator, ie an electrode insulation 46 .
  • the (spray) electrode 45 hangs downwards into the interior of the filter device 4 so that it can vibrate.
  • the electrode 45 can, for example, vibrate back and forth transversely to the longitudinal axis of the electrode 45 .
  • a cage 48 simultaneously serves as a counter-electrode and as a cleaning mechanism for the filter device 4.
  • the cage 48 is connected to ground or earth potential. Due to the prevailing potential difference, the exhaust gas flowing in the filter device 4 is filtered, cf. the arrows S6, as explained above. In the case of cleaning of the filter device 4, the electrode 45 is switched off.
  • the cage 48 preferably has an octagonal regular cross-sectional profile, as can be seen, for example, in FIG 9 can be taken.
  • the cage 48 can preferably be laser cut during manufacture.
  • the flue gas flows through the turning chamber 34 into the inlet 44 of the filter device 4.
  • the (optional) filter device 4 is optionally provided fully integrated in the boiler 11, whereby the wall surface facing the heat exchanger 3 and flushed through by the heat exchange medium is also used for heat exchange from the direction of the filter device 4, whereby the efficiency of the system 1 is further improved. In this way, at least part of the wall of the filter device 4 can be flushed with the heat exchange medium, with the result that at least part of this wall is cooled with boiler water.
  • the cleaned exhaust gas flows out of the filter device 4 at the filter outlet 47, as indicated by the arrows S7. After leaving the filter, part of the exhaust gas is returned to the primary combustion zone 26 via the recirculation device 5 . This will also be explained in more detail later. The remaining part of the exhaust gas is conducted out of the boiler 11 via the exhaust gas outlet 41 .
  • the ash removal device 7 is arranged in the lower part of the boiler 11 .
  • the ash that is separated and falling out of the combustion chamber 24, the boiler tubes 32 and the filter device 4, for example, is discharged laterally out of the boiler 11 via an ash discharge screw 71.
  • the drive unit 72 which has an optional gear and a freewheel 73 , is provided for driving the ash removal 7 and a cleaning device 9 (see later).
  • a thrust member 74 which will be explained in more detail later, is used with a crank element 77 as a transmission element between the motor and other elements of the cleaning device 9 (cf. also 13 et seq.).
  • the mechanical components of the cleaning device are mounted or held in a frame 76 which is welded to the boiler base 12, for example.
  • the combustor 24 and boiler 11 of this embodiment were calculated using CFD simulations. Furthermore, practical experiments were carried out to confirm the CFD simulations. The starting point for the considerations were calculations for a 100 kW boiler, although a power range from 20 to 500 kW was taken into account.
  • the flow processes can be laminar and/or turbulent, accompanied by chemical reactions, or it can be a multi-phase system.
  • CFD simulations are therefore well suited as a design and optimization tool.
  • CFD simulations were used to optimize the fluidic parameters in such a way that the objects of the invention listed above are achieved.
  • the mechanical design and dimensioning of the boiler 11, the combustion chamber 24, the secondary air nozzles 291 and the combustion chamber nozzle 203 were largely defined by the CFD simulation and also by associated practical experiments.
  • the simulation results are based on a flow simulation taking heat transfer into account.
  • the design of the combustor shape is important in order to be able to meet the task requirements.
  • the shape and geometry of the combustion chamber should ensure the best possible turbulent mixing and homogenization of the flow over the cross section of the flue gas duct, minimization of the combustion volume, as well as a reduction in the excess air and the recirculation ratio (efficiency, operating costs), a reduction in the CO and CxHx Emissions, NOx emissions, dust emissions, a reduction in local temperature peaks (fouling and slagging) and a reduction in local flue gas velocity peaks (material stress and erosion) can be achieved.
  • the 4 showing a partial view of the 2 is, and the figure 5 , which is a sectional view through the boiler 11 along the vertical section line A2, represent a combustion chamber geometry that meets the above-mentioned requirements for biomass heating systems over a wide power range of, for example, 20 to 500 kW.
  • the vertical section line A2 can also be understood as the middle or central axis of the oval combustion chamber 24 .
  • both the geometries of the primary combustion zone 26 and the secondary combustion zone 27 of the combustion chamber 24 are optimized with these values.
  • the specified size ranges are ranges with which the requirements are (approximately) fulfilled as well as with the specified exact values.
  • a chamber geometry of the primary combustion zone 26 and the combustion chamber 24 can preferably be defined using the following basic parameters: A volume with one oval horizontal Floor space with the dimensions from 380 mm + ⁇ 60 mm preferably + ⁇ 30 mm ⁇ 320 mm + ⁇ 60 mm preferably + ⁇ 30 mm , as well as one Height from 538 mm + ⁇ 80 mm preferably + ⁇ 50 mm .
  • the size information given above can also be applied to boilers in other output classes (e.g. 50 kW or 200 kW) scaled in relation to one another.
  • the volume defined above can have an upper opening in the form of a combustion chamber nozzle 203, which is provided in the secondary combustion zone 27 of the combustion chamber 24, which has a combustion chamber slope 202 protruding into the secondary combustion zone 27, which preferably contains the heat exchange medium 38.
  • Combustion chamber slope 202 reduces the cross section of secondary combustion zone 27.
  • Combustion chamber slope 202 is inclined by an angle k of at least 5%, preferably by an angle k of at least 15% and even more preferably by at least an angle k of 19% with respect to an imaginary Horizontal or straight combustion chamber ceiling H (cf. the dashed horizontal line H in 4 ) intended.
  • a combustion chamber cover 204 is provided, likewise inclined in the direction of the inlet 33 .
  • the combustion chamber 24 in the secondary combustion zone 27 thus has the combustion chamber ceiling 204 which is provided inclined upwards in the direction of the inlet 33 of the heat exchanger 3 .
  • This combustion chamber ceiling 204 extends in section 2 at least largely straight or rectilinear and inclined.
  • the angle of inclination of the straight or flat combustion chamber ceiling 204 can preferably be 4 to 15 degrees relative to the (fictitious) horizontal.
  • a further (ceiling) slope is provided in the combustion chamber 24 in front of the inlet 33, which forms a funnel together with the combustion chamber slope 202.
  • This funnel turns the swirling or eddy flow directed upwards to the side and deflects this flow more or less horizontally. Due to the already turbulent upward flow and the funnel shape in front of the inlet 33, it is ensured that all heat exchanger tubes 32 or boiler tubes 32 are flown evenly, whereby an evenly distributed flow of the flue gas in all boiler tubes 32 is ensured. This optimizes the heat transfer in the heat exchanger 3 considerably.
  • the combination of the vertical and horizontal inclines 203, 204 in the secondary combustion zone in combination as the inflow geometry in the convective boiler can achieve a uniform distribution of the flue gas over the convective boiler tubes.
  • the combustion chamber slope 202 serves to homogenize the flow S3 in the direction of the heat exchanger 3 and thus the flow through the boiler tubes 32. This causes the flue gas to be distributed as evenly as possible to the individual boiler tubes in order to optimize the heat transfer there.
  • the combination of the inclines with the inflow cross section of the boiler rotates the flue gas flow in such a way that the flue gas flow or the flow rate is distributed as evenly as possible over the respective boiler tubes 32 .
  • the combustion chamber 24 is provided without dead corners or dead edges.
  • the primary combustion zone 26 of the combustion chamber 24 can comprise a volume which preferably has an oval or approximately circular horizontal cross-section on the outer circumference (such a cross-section is shown in 2 marked with A1 as an example).
  • This horizontal cross section can also preferably represent the base area of the primary combustion zone 26 of the combustion chamber 24 .
  • the combustion chamber 24 can have an approximately constant cross section over the height indicated by the double arrow BK4.
  • the primary combustion zone 24 can have an approximately oval-cylindrical volume.
  • the side walls and base (grate) of the primary combustion zone 26 may be perpendicular to one another.
  • the bevels 203, 204 described above can be provided as integrated walls of the combustion chamber 24, with the bevels 203, 204 forming a funnel which opens into the inlet 33 of the heat exchanger 33 and has the smallest cross section there.
  • the horizontal cross section of the combustion chamber 24 and in particular of the primary combustion zone 26 of the combustion chamber 24 can likewise preferably be of regular design. Further, the horizontal cross-section of the combustor 24, and particularly the primary combustion zone 26 of the combustor 24, may preferably be a regular (and/or symmetrical) ellipse.
  • the horizontal cross section (the outer circumference) of the primary combustion zone 26 can be made constant over a predetermined height (for example, 20 cm).
  • An oval-cylindrical primary combustion zone 26 of the combustion chamber 24 is thus provided in the present case, which, according to CFD calculations, enables a significantly more uniform and better air distribution in the combustion chamber 24 than in the case of rectangular combustion chambers of the prior art.
  • the lack of dead spaces also avoids zones in the combustion chamber with poor air flow, which increases efficiency and reduces slag formation.
  • the nozzle 203 in the combustion chamber 24 is designed as an oval or approximately circular constriction in order to further optimize the flow conditions.
  • This optimized nozzle 203 bundles the flue gas-air mixture flowing upwards rotating and ensures better mixing, preservation of the eddy currents in the Secondary combustion zone 27 and thus for complete combustion. This also minimizes the excess air required. This improves the combustion process and increases efficiency.
  • the combination of the secondary air nozzles 291 explained above and the eddy currents induced thereby with the optimized nozzle 203 serves in particular to bundle the flue gas/air mixture rotating upwards. This ensures at least approximately complete combustion in the secondary combustion zone 27.
  • a turbulent or swirling flow is bundled through the nozzle 203 and directed upwards, with the result that this flow extends further upwards than is usual in the prior art.
  • this is due to the reduction in the distance of the swirling air flow to the rotation or swirl center axis, which is forced by the nozzle 203 (compare analogously to the physics of the pirouette effect).
  • the combustion chamber slope 202 of 4 which without a reference number in the 2 and 3 can be seen and where the combustion chamber 25 (or its cross-section) tapers at least approximately linearly from bottom to top, according to CFD calculations ensures that the flue gas flow in the direction of the heat exchange device 4 is made more uniform, which means that its efficiency can be improved.
  • the horizontal cross-sectional area of the combustion chamber 25 tapers from the beginning to the end of the combustion chamber slope 202, preferably by at least 5%.
  • the combustion chamber slope 202 is provided on the side of the combustion chamber 25 towards the heat exchange device 4 and is provided rounded off at the point of maximum narrowing.
  • combustion chamber cover 204 which runs obliquely upwards towards the inlet 33 and diverts the eddy currents in the secondary combustion zone 27 laterally, thereby making their flow velocity distribution more uniform.
  • the inflow or deflection of the flue gas flow in front of the tube bundle heat exchanger is designed in such a way that an uneven flow of the tubes is avoided as far as possible, whereby temperature peaks in individual boiler tubes 32 can be kept low and thus the heat transfer in the heat exchanger 4 can be improved (best possible use of the heat exchanger surfaces). . As a result, the efficiency of the heat exchange device 4 is improved.
  • the gaseous volume flow of the flue gas is conducted through the inclined combustion chamber wall 203 at a uniform speed (even in the case of different combustion states) to the heat exchanger tubes or the boiler tubes 32.
  • This effect is further intensified by the sloping combustion chamber ceiling 204, with a funnel effect being brought about.
  • the result is a uniform heat distribution of the heat exchanger surfaces affecting the individual boiler tubes 32 and thus an improved use of the heat exchanger surfaces.
  • the exhaust gas temperature is thus reduced and the efficiency increased.
  • the flow distribution is particularly at the in the 3 shown indicator line WT1 much more evenly than in the prior art.
  • the line WT1 represents an entry surface for the heat exchanger 3.
  • the indicator line WT3 indicates an exemplary cross-sectional line through the filter device 4, in which the flow is set up as homogeneously as possible or is approximately evenly distributed over the cross-section of the boiler tubes 32 (due to of flow screens at the entrance of the filter device 4 and due to the geometry of the turning chamber 35).
  • a uniform flow through the filter device 3 or the last boiler train minimizes strand formation and thereby also optimizes the separation efficiency of the filter device 4 and the heat transfer in the biomass heating system 1.
  • an ignition device 201 is provided in the lower part of the combustion chamber 25 on the fuel bed 28 . This can cause initial ignition or re-ignition of the fuel.
  • the ignition device 201 can be a glow igniter.
  • the ignition device is advantageously stationary and horizontally offset laterally to the location of the introduction of the fuel.
  • a lambda probe (not shown) can (optionally) be provided after the exit of the flue gas (ie, after S7) from the filter device.
  • a controller (not shown) can use the lambda probe to detect the respective calorific value.
  • the lambda probe can thus ensure the ideal mixing ratio between the fuels and the oxygen supply. Despite different fuel qualities, the result is high efficiency and higher efficiency.
  • the fuel bed 28 shown shows a rough fuel distribution due to the feeding of the fuel from the right side of the figure 5 .
  • combustion chamber nozzle 203 is shown in which a secondary combustion zone 27 is provided and which accelerates and focuses the flue gas flow. As a result, the flue gas flow is better mixed and can burn more efficiently in the post-combustion zone 27 or secondary combustion zone 27 .
  • the area ratio of the combustion chamber nozzle 203 is in a range from 25% to 45%, but is preferably 30% to 40%, and is, for example for a 100 kW biomass heating system 1, ideally 36% +/- 1% (ratio of the measured input area to the measured exit area of the nozzle 203).
  • the 6 shows a three-dimensional sectional view (obliquely from above) of the primary combustion zone 26 and the isolated part of the secondary combustion zone 27 of the combustion chamber 24 with the rotary grate 25, and in particular the special design of the combustion chamber bricks 29.
  • the 7 shows according to 6 an exploded view of the combustion chamber bricks 29.
  • the views of 6 and 7 can preferably with the dimensions listed above 4 and 5 be executed. However, this is not necessarily the case.
  • the chamber wall of the primary combustion zone 26 of the combustor 24 is provided with a plurality of combustor bricks 29 in a modular construction which, among other things, facilitates manufacture and maintenance. Maintenance is facilitated in particular by the possibility of removing individual combustion chamber bricks 29.
  • Form-fitting grooves 261 and projections 262 are provided in order to create a mechanical and largely airtight connection, in order in turn to prevent the ingress of disturbing external air.
  • every two at least largely symmetrical combustion chamber bricks (with the possible exception of the openings for the secondary air or the recirculated flue gas) form a complete ring.
  • three rings are preferably stacked on top of one another in order to form the primary combustion zone 26 of the combustion chamber 24 which is oval-cylindrical or alternatively at least approximately circular (the latter is not shown).
  • Three further combustion chamber bricks 29 are provided as the upper closure, with the annular nozzle 203 being supported by two retaining bricks 264 which are placed on the upper ring 263 in a form-fitting manner. All bearing surfaces 260 have grooves 261 either for mating projections 262 and/or for the insertion of suitable sealing material.
  • the mounting stones 264 which are preferably symmetrical, can preferably have an inwardly inclined bevel 265 in order to make it easier for fly ash to be swept away onto the rotary grate 25.
  • the lower ring 263 of the combustion chamber bricks 29 rests on a base plate 251 of the rotary grate 25 . Ash is increasingly deposited on the inner edge between this lower ring 263 of the combustion chamber bricks 29 , which advantageously independently and advantageously seals this transition during operation of the biomass heating system 1 .
  • the openings for the recirculation nozzles 291 or secondary air nozzles 291 are provided in the middle ring of the combustion chamber bricks 29 .
  • the secondary air nozzles 291 are provided at least approximately at the same (horizontal) height of the combustion chamber 24 in the combustion chamber bricks 29 .
  • Three rings of combustor bricks 29 are provided here, as this represents the most efficient way of manufacture and also of maintenance. Alternatively, 2, 4 or 5 such rings can also be provided.
  • the combustion chamber bricks 29 are preferably made of high-temperature silicon carbide, which makes them very wear-resistant.
  • the combustion chamber bricks 29 are provided as shaped bricks.
  • the combustion chamber bricks 29 are shaped in such a way that the interior volume of the primary combustion zone 26 of the combustion chamber 24 has an oval horizontal cross section, which means that dead corners or dead spaces, which are usually not optimally flown through by the flue gas/air mixture, are avoided by an ergonomic shape, whereby the fuel present there is not is optimally burned. Due to the present shape of the combustion chamber bricks 29, the flow of primary air through the grate 25, which also suits the distribution of the fuel over the grate 25, and the possibility of unhindered turbulent flows is improved; and consequently the efficiency of combustion is improved.
  • the oval horizontal cross section of the primary combustion zone 26 of the combustion chamber 24 is preferably a point-symmetrical and/or regular oval with the smallest inside diameter BK3 and the largest inside diameter BK11.
  • Turbulators increase the formation of turbulence in the boiler tubes 32, which reduces the flow rate, increases the residence time of the flue gas in the boiler tube 32 and thus increases the efficiency of the heat exchange.
  • the boundary layer of the flow on the pipe wall is broken up, which improves heat transfer.
  • the more turbulent the flow the greater the pressure loss.
  • the heat exchanger 3 has a vertically arranged bundle of boiler tubes 32, each boiler tube 32 preferably being provided with both a spring and a band or spiral turbulator.
  • the respective spring turbulator 36 preferably extends over the entire length of the respective boiler tube 32 and is designed in the shape of a spring.
  • the respective band turbulator 37 preferably extends over about half Length of the respective boiler tube 32 and has a spiral in the axial direction of the boiler tube 32 extending band with a material thickness of 1.5 mm to 3 mm. Furthermore, the respective band turbulator 37 can also be approximately 35% to 65% of the length of the respective boiler tube 32.
  • Each band turbulator 37 is preferably disposed with one end at the downstream end of each boiler tube 32 .
  • the combination of spring and ribbon or spiral turbulator can also be referred to as a double turbulator.
  • both ribbon and spiral turbulators are shown.
  • the band turbulator 37 is located within the spring turbulator 36 .
  • only one type of turbulator can be used as a cleaning element, in particular for cleaning purposes.
  • a cleaning shaft 92 can also be seen, which extends transversely to the viewing direction.
  • Band turbulators 37 are provided because the band turbulator 37 increases the turbulence effect in the boiler tube 32 and causes a more homogeneous temperature and velocity profile viewed over the tube cross-section, while the tube without a band turbulator preferably forms a hot streak with higher velocities in the center of the tube, which extends to the outlet of the boiler tube 32, which would adversely affect the heat transfer efficiency.
  • the band turbulators 37 in the lower area of the boiler tubes 32 thus improve the convective heat transfer.
  • 22 boiler tubes with a diameter of 76.1 mm and a wall thickness of 3.6 mm can be used.
  • the pressure drop can be less than 25 Pa.
  • the spring turbulator 36 ideally has an outer diameter of 65 mm, a pitch of 50 mm, and a profile of 10 ⁇ 3 mm.
  • the band turbulator 37 can have an outer diameter of 43 mm, a pitch of 150 mm and a profile of 43 ⁇ 2 mm.
  • a sheet metal thickness of the band turbulator can be 2 mm.
  • the desired target temperature at the outlet of the boiler tubes 32 can preferably be between 100 and 160 degrees Celsius at rated output.
  • the 9 shows a cleaning device 9 with which both the heat exchanger 3 and the filter device 4 can be cleaned (off) automatically.
  • the 9 shows the cleaning device from the boiler 11 for the sake of clarity.
  • the cleaning device 9 relates to the entire boiler 11 and thus relates to the convective part of the boiler 11 and also the last boiler pass, in which the electrostatic filter device 4 can optionally be integrated.
  • the cleaning device 9 has levers 921 which can transmit forces to two cleaning shafts 92 , the cleaning shafts 92 in turn being mounted in a shaft mount 93 .
  • the cleaning shafts 92 can preferably also be mounted rotatably at another location, for example at the remote ends.
  • the cleaning shafts 92 have extensions 94 to which the cage 48 of the filter device 4 and the turbulator holders 95 are connected and mounted via joints or via rotary bearings. In 9 only an angled extension 94 is shown as an example. However, the extension 94 or the extensions can also be rectilinear extend.
  • levers 921 have at their distal end (remote from the cleaning shaft 92) lever pins 922 which protrude in the direction of the axis of the cleaning shaft 92. These lever pins engage in slots or elongated holes 743, also referred to as lever pin holes 743, which will be explained later.
  • the turbulator mount 95 is in 10 highlighted and enlarged.
  • the turbulator mount 95 is designed in the manner of a comb and is preferably designed to be horizontally symmetrical.
  • the turbulator holder 95 is designed as a flat piece of metal with a material thickness in the thickness direction D of between 2 and 5 mm.
  • the turbulator mount 95 has two pivot bearing mounts 951 on its underside for connection to pivot bearing journals (not shown) of the extensions 94 of the cleaning shafts 92 .
  • Pivot mounts 951 may have horizontal play in which pivot pins or pivot linkage 955 can reciprocate as extensions 94 lever-like move with cleaning shaft 92 as the axis of rotation as cleaning shaft 92 rotates.
  • the extensions 94 can, for example, extend away from the cleaning shaft 92 in the lateral direction of the boiler 11 .
  • the turbulator mount 95 and/or the cage 48 and/or the turbulators 36/37 can be attached to the distal end of the extensions 94, for example. This attachment can be done via a joint or, as described above, via a bearing, or via a game.
  • the extensions 94 also serve as levers. A rotation is converted into a stroke and vice versa.
  • the extensions 94 of the cleaning shaft 92 extend radially from the cleaning shaft 92 so that they raise or lower the turbulator mount 95 (and the cleaning cage 94) as the cleaning shaft rotates.
  • the extensions are provided on the cleaning shaft 92 in such a way that the rotation of the cleaning shaft 92 is converted into at least a partial vertical stroke and vice versa.
  • the weight of the parts or elements acting on the cleaning shaft 92 can be more than 10 kilograms, preferably more than 30 kilograms, in order to generate a strong torque on the central axis of the cleaning shaft 92 .
  • the cleaning shaft 92 or the cleaning shafts 92 serve as a transmission element/s between the cleaning elements, for example the turbulators 36, 37, and a thrust element 74, which will be explained later in relation to the Figures 13 to 24 will be explained in more detail.
  • Vertically protruding extensions 952 also have a plurality of recesses 954 in and with which the double turbulators 36, 37 can be attached.
  • the recesses 954 can be at a distance from one another which corresponds to the pitch of the double turbulators 36, 37.
  • passages 953 for the flue gas can preferably be arranged in the turbulator holder 95 in order to optimize the flow from the boiler tubes 32 into the filter device 4 . Otherwise the flat metal would be at right angles to the flow and impede it too much.
  • the spiral automatically rotates under its own weight into the receptacle of the turbulator holder 95 (which can also be referred to as the receiving rod) and is thus fixed and secured. This makes assembly much easier.
  • the figures 11 and 12 show the cleaning mechanism 9 without the cage 48 in two different states.
  • the cage mount 481 can be seen better here.
  • FIG. 11 shows the cleaning mechanism 9 in a first (rest) state, with both the turbulator mounts 95 and the cage mount 481 in a lower position.
  • a two-armed hammer 96 with a stop head 97 is attached to one of the cleaning shafts 92 .
  • the impact lever 96 can also be provided with one or more arms.
  • the impact lever 96 with the stop head 97 is set up in such a way that it can be moved to the end of the (spray) electrode 45 or can strike against it.
  • the impact process can advantageously take place quickly and with a great deal of energy.
  • the impact lever 96 with the stop head 97 can strike the end of the (spray) electrode 45, for example during the transition from the first state to the second state.
  • This striking at the free (ie not suspended) end of the (spray) electrode 45 has the advantage over conventional vibrating mechanisms (in which the electrode is moved on its suspension) that the (spray) electrode 45 according to its vibration characteristics after the excitation the striking itself can vibrate (ideally freely).
  • the type of attack determines the oscillations or oscillation modes of the (spray) electrode 45 Longitudinal vibration to be struck.
  • the (spray) electrode 45 can also be located on the side (in the figures 11 and 12 be struck, for example, from the direction of arrow V), so that it oscillates transversely.
  • the (spray) electrode 45 can be the (spray) electrode 45 (as present in figures 11 and 12 shown) are attached at the end from a slightly laterally offset direction from below.
  • a plurality of different vibration modes are generated in the (spray) electrode 45 (by striking), which advantageously add up in the cleaning effect and improve the efficiency of the cleaning.
  • the shearing effect of the transverse vibration on the surface of the (spray) electrode 45 can improve the cleaning effect.
  • an impact or a shock wave can occur in the elastic spring electrode 45 in the longitudinal direction of the electrode 45, which is preferably designed as an elongated plate-shaped rod.
  • a transverse vibration of the (spray) electrode 45 can also occur due to the acting transverse forces (which are aligned transversely or at right angles to the direction of the longitudinal axis of the electrode 45).
  • a shock wave and/or longitudinal wave combined with a transverse vibration of the electrode 45 can again lead to improved cleaning of the electrode 45.
  • the cleaning device 9 can be manufactured simply and inexpensively in the manner described and has a simple and low-wear structure.
  • the cleaning device 9 is set up with the drive mechanism in such a way that ash residues are advantageously already removed from the first train of the boiler tubes 32 can be cleaned by the turbulators and can fall down.
  • the cleaning device 9 is installed in the lower, so-called “cold area” of the boiler 11, which also reduces wear, since the mechanics are not exposed to very high temperatures (i.e. the thermal load is reduced).
  • the cleaning mechanism is installed in the upper area of the system, which correspondingly disadvantageously increases wear.
  • FIG 13 shows a cross-sectional view through a biomass heating system 1 according to a modification of the biomass heating system of FIG 1 and 2 , which is shown viewed from the side view S.
  • the modification of 13 of the biomass heating system 1 of 1 concerns minor changes to the number of boiler tubes 32 and the dimensioning of the biomass heating system 1, as well as a further improvement in the cleaning device 9 and the ash removal 7.
  • the biomass heating system 1 of 13 has a boiler 11, a combustion device 2 with a combustion chamber 24, a boiler base 12 (this is provided at the bottom) and a movable ash container 79 for receiving the combustion residues conveyed out of the biomass heating system 1 by the ash discharge screw 71.
  • the arrow S indicates the side view of the biomass heating system 1
  • the arrow V indicates the front view of the biomass heating system 1.
  • the biomass heating system 1 of 13 further has a heat exchanger 3 with turbulators 36, 37, which are arranged to be movable in the height direction or in the axial direction of the boiler tubes 32.
  • turbulators 36, 37 in the boiler tubes 32 can be moved back and forth.
  • Combustion residues are removed from the boiler tubes 32 by the movement of the turbulators 36, 37, mechanically detached from the walls of the boiler tubes 32, for example scraped off or detached by impact (more on this later).
  • the combustion residues fall down into the conveyor area of the ash discharge screw 71, are collected there, and are in the 13 transported to the right out of the biomass heating system 1.
  • a filter device 4 which has a (spray) electrode 45 and a (cleaning) cage 48 as a counter-electrode.
  • the cage 48 is arranged in such a way that when it moves up and down it mechanically loosens the wall of the filter device, for example scrapes it off or releases it by impact (more on this later).
  • the combustion residues fall down through the filter inlet 44 into the conveying area of the ash discharge screw 71, are collected there, and are in the 13 transported to the right out of the biomass heating system 1.
  • an improved cleaning device 4 is provided, which is driven by a drive unit 72, preferably a single drive unit.
  • the drive unit can be an electric motor 72 .
  • the electric motor 72 is provided as the sole drive for all components of the cleaning device 9 including the ash removal 7, which means that the present overall concept is structurally advantageous (space-saving, inexpensive, robust).
  • the electric motor 72 can also be, for example, an electric motor with a gear that can provide more than three revolutions per minute with a torque of more than 50 Nm, preferably more than four revolutions per minute with a maximum torque of 100 Nm.
  • the electric motor 72 can also have an (internal or external) freewheel 73 .
  • the transmission of the electric motor can be integrated with the freewheel 73 .
  • a crank element 77 (explained later) can preferably be mounted via an axle through the freewheel 73, for example a ball bearing freewheel.
  • the axis can preferably correspond to the axis of the ash discharge screw 71, whereby the crank element 77 and the ash discharge screw 71 are driven together via the freewheel.
  • the central axis of this common axis is denoted as axis of rotation 773 .
  • the freewheel can advantageously also be used for reverse travel of the ash discharge screw 71, which is required, for example, in the case of solid bodies jammed in the ash discharge screw 71, in order to remove the solid bodies.
  • a push member 74 is shown in section, which can be moved, among other things, by the electric motor 72 via a crank element 77 .
  • the electric motor 72 and other moving elements of the cleaning device 9 can be fixed or supported by immovable elements of the boiler 11, which are referred to collectively as the frame 76.
  • a sensor 75 is provided for detecting the movement or the position of the pushing member 74 .
  • the 14 shows a plan view of an exempt push member 74 of FIG 13 from the rear of the biomass heating system 1 the 13 .
  • the 15 shows a plan view of the exempt pusher member 74 of FIG 14 from the rear of the biomass heating system 1 together with other parts of the biomass heating system 1 of the 13 .
  • the thrust member 74 is explained as an individual part (cf. 14 ), with the functional explanation of the thrust member 74 then (cf. 15 ).
  • the thrust member 74 can be provided (roughly) in the form of a plate, with which in 14 a plan view of this plate-shaped element is shown.
  • the pushing member 74 can be made of a metal plate that is at least 5 mm thick, preferably at least 1 cm thick.
  • the thrust element can be cut out as a solid plate, for example by means of a laser cutting process.
  • the thrust member can be provided in one piece. The thrust member 74 is therefore correspondingly robust and can also withstand the corresponding forces acting in the processes and movements explained later.
  • the pushing member 74 has a special shape, as explained below.
  • the thrust member 74 has two guide holes 742, which are provided as an elongated hole or slot. Alternatively, however, the thrust member (not shown) can also have only one or more than two guide holes.
  • the lengthwise direction of the guide holes 742 may be horizontal with respect to installation of the pushing member 74 in the boiler 11 . Also, the length direction of the guide holes 742 may be provided in the lateral direction of the kettle 11.
  • the guide holes 742 are used to movably support the thrust member 74, which later with respect to 15 is explained in more detail.
  • the push member 74 preferably approximately or exactly in the middle in relation to the width extension of the push member 74, has an opening 741 for receiving a force-exerting element (will be explained later with reference to FIG 15 explained in more detail).
  • the opening 741 is provided as an elongated opening with rounded ends.
  • the thrust member 74 has two pivot holes 743, preferably lever pivot holes 743.
  • the thrust member 74 (not shown) can also have only one or more than two pivot holes.
  • the lengthwise direction of the pivot holes 743 with respect to the boiler 11 may be vertical.
  • a "hole” of the thrust member can be a hole completely surrounded by material, or for example a slot which is open at one end.
  • the thrust member 74 also has a stop 744, which will be explained in more detail later.
  • the length direction(s) of the guide holes 742 is preferably perpendicular to the length directions of the pin holes 753 .
  • This thrust member 74 serves as part of a (pulse-generating) transmission of the biomass heating system, with which the movement parameters of the individual parts of the cleaning device 9 can advantageously be changed or adjusted.
  • the rotational movement of the drive unit 72 with the thrust member 74 is converted into jerky or accelerated movements of cleaning elements of the biomass heating system 1, for example the cage 48, the turbulators 36, 37 and/or the impact lever 96.
  • guide pins 711 which are used for the movable mounting of the thrust member 74.
  • the guide pins 711 extend into or out of the plane of the paper.
  • the guide pins 711 are provided in a stationary manner in or on the boiler 11 and, together with the guide holes 742, specify the freedom of movement of the thrust member 74.
  • a movement of the guide pins 711 in the guide holes 742 is indicated by the two double arrows in the guide holes 742.
  • the thrust member can move back and forth in the direction of the double arrow HR.
  • the thrust member 74 is therefore provided so that it can be displaced laterally with respect to the boiler 11 .
  • the thrust member 74 is provided so that it can be displaced in a straight line.
  • the thrust member can be moved in a linear translational movement.
  • the possible length of the movement of the thrust member 74 is indicated by the double arrows FL, this length resulting from the length of the guide holes 742 results.
  • the movement is generated at least to a large extent in the thrust direction by the drive unit 72 (not shown), for example an electric motor, which drives a freewheel 73 (not shown) and a crank element 77 .
  • the crank element 77 can be provided, for example, as a crank disk with a (e.g. rod-shaped) crank extension 771, or alternatively as a crank lever with a crank extension 771.
  • the crank element 77 rotates or cranks about the axis of rotation 773 of the crank element 77.
  • the central axis of the crank extension 771 is in 15 perpendicular to the plane of the paper.
  • the central axis can also be provided at a slight angle to the plane of the paper.
  • a roller 772 can optionally be provided on the crank extension 771 to reduce wear and for better running of the mechanism, with the roller 772 in 15 is shown in dashed lines
  • crank extension 771 and the optional roller 772 protrude through the opening 741 of the push member 74 therethrough.
  • the crank extension 771 moves in the opening 741 of the push member 74.
  • the crank extension 771 or the roller 772 can rest against the edges of the opening 741. In the case shown here, the outside of the roller 772 rests against the inside edges of the opening 741 .
  • the effective radius of crank movement of the crank element 77 is indicated by the arrow RH emanating from the axis of rotation 773 and the associated dashed line (i.e. this is the outer radius of the roller in a circular movement of the crank element 77 with the roller 772), with which the diameter of the Deflection by crank member 77 is twice the radius RH.
  • crank element 77 The direction of rotation of the crank element 77 is in 15 indicated by the arrow DR.
  • the length FL can be greater than or equal to the radius RH times two.
  • the special geometry of the opening 741 (among others) can lead to the impulse effect of the present cleaning device.
  • a hexagon nut and a washer for fixing the roller 772 in the opening 741 of the push member 74 are shown but not specified in more detail.
  • the opening 741 has a width SB that is equal to or larger than the width of the pulley 772 or equal to or larger than the width of the crank extension 771 (without the pulley).
  • width SB push element opening width SB
  • the width SB is slightly larger than the diameter of the roller 771. This can preferably provide play to minimize locking.
  • the length LB (pusher opening length) of the opening 741 may be equal to or greater than twice the radius RH.
  • crank member 77 and the opening 741 are provided such that the crank extension 771 and the roller 772 can move in the opening 741 to generate thrust, respectively.
  • the course of movement is described in more detail with reference to the figures below, to which reference is made.
  • a damping element 78 for example a spiral spring or a rubber element, is also provided.
  • the damping element 78 is attached to the boiler 11 with a damping element fixation 781 .
  • the damping element fixation 781 is thus provided immovably.
  • the damping element 78 is thus referring to 15 fixed on its left side.
  • a stop 744 for the damping element 78 is provided on the side of the thrust member 74 .
  • the damping element 78 essentially dampens or decelerates the movement or acceleration of the thrust member 74 in the direction of the impulse. This serves to minimize closure and to dampen noise.
  • the kinetics of the thrust member and thus of the cleaning device 9 can also advantageously be adjusted.
  • the central axis of a spiral spring is provided as a damping element 78 at least largely parallel to the directions of movement HR of the thrust member 74 .
  • lever pin 922 of the lever 921 there are two elements that are moved or move with the pusher 74: the lever pin 922 of the lever 921. It should be noted that alternatively only one Element or lever pin 922 can be provided with a corresponding hole.
  • lever pins 922 and the levers 921 are explained in more detail below.
  • the guide pins 711 are also the ends of the axes of the cleaning shafts 92, the cleaning shafts 92 and thus the guide pins 711 being mounted in the boiler 11 in a stationary manner.
  • the levers 921 shown in phantom are attached to the cleaning shafts 92 and the cleaning shafts 92 can be rotated by means of the levers 921 and vice versa.
  • the levers 921 can be designed in the form of rods, for example.
  • the Levers 921 of 15 are also in 13 shown.
  • lever pins 922 which extend through the lever pin holes 743 .
  • the lever pins 922 can move in the lever pin holes 743 in the direction of the double arrows (up and down) next to them.
  • the levers 921 can move in the respective angular range S based on a back and forth movement of the push member 74 .
  • the fulcrum pins 922 move (ie, reciprocating movement of the pusher member 74) along the circular segment lines that are associated with the respective angle S in 15 are specified.
  • the thrust member 74 is further alternately in the in 15 specified thrust direction and also in 15 moves back and forth in the direction indicated. This and the interaction of the crank element 77, the pusher member 74 and the cleaning shafts 92 is described below with reference to FIG Figures 16 to 23 explained.
  • FIGs 16 to 23 show a total of four states of the cleaning device 9, each with two consecutive figures.
  • the 16 shows a rear view of the biomass heating system 1 of 13 and thus the thrust member 74 of 14 and 15 in the larger context of the biomass heating system 1.
  • 17 shows a corresponding oblique view from behind of the biomass heating system 1 of FIG 13 in the initial or idle state with a view of the biomass heating system 1.
  • 20 shows a rear view of the biomass heating system 1 of 13 and the thrust member 74 of 14 and 15 in the maximum stroke state of the cleaning device 9.
  • 21 shows a corresponding oblique view from behind of the biomass heating system 1 of FIG 13 in the overrun condition of the cleaning device 9 with a view of the biomass heating system 1.
  • 22 shows a corresponding rear view of the biomass heating system 1 of FIG 13 and the thrust member 74 of 14 and 15 in the case of the cleaning device 9.
  • 23 shows a corresponding oblique view from behind of the biomass heating system 1 of FIG 13 in the case of the cleaning device 9 with a view of the biomass heating system 1.
  • the figures 16 and 17 show the cleaning device 9 in an initial/resting state. In this state, the normal operation of the biomass heating system takes place without cleaning having to take place. In this respect, the cleaning device can also remain in this idle state for a longer period of time. This state is therefore also the initial state for a cleaning process or the present cleaning method.
  • the crank element 77 In the initial state, the crank element 77 is in a first rotational position (also referred to as the initial position), which is in 16 is indicated schematically by the dot-dash line, which extends from the axis of rotation 773 of the Crank element 77 extends to the left.
  • the guide pins 711 are located in the guide holes 742 on the right side of the 16 .
  • the thrust member 74 is at least largely deflected in the direction of the impulse, ie viewed from the front in the direction of the right-hand side of the biomass heating system 1 .
  • the sensor 75 for example a magnetic/inductive sensor, can detect the presence of the thrust member 74 and transmit it to a control device (not shown), for example.
  • the biomass heating system 1 can thus detect the presence of the idle state or the initial state.
  • the damping element 78 is compressed and rests against the stop for the damping element 744 .
  • the two levers 921 are in a basic position.
  • a cleaning element can be, for example, the cage 48 and/or a single turbulator or a plurality of turbulators 36, 37 and/or the impact lever 96.
  • these cleaning elements are in a position in which the cleaning elements are arranged at the bottom, at least largely in relation to their vertical range of motion.
  • This bottom position is in 17 indicated with H1 by way of example in relation to the upper end of the turbulators.
  • the cage 48 is in a lower position. This position is relative to an upper end of the cage 48 in 17 also indicated by H1, the coincidence of the two heights of the cleaning elements being merely coincidental in the present case.
  • the cage 48 and the turbulators 36 and 37 can generally also be arranged at different heights.
  • the figures 18 and 19 show the cleaning device 9 in an overrun state. At the beginning of this state, a cleaning is started or continued.
  • the drive unit 72 rotates the crank element 77 from its starting position or first crank rotational position (in short: first position) in the direction of rotation DR and thus pushes the thrust member 74 in the thrust direction (in 18 to the right, viewed from the front of the biomass heating system 1 to the left).
  • crank member 77 In the pushing state, the crank member 77 is between its initial position and that later with respect to FIG 20 explained self-running starting position of the crank element 77. In 18 one of these possible positions is indicated by way of example by the dot-dash line which extends downwards from the axis of rotation 773 of the crank element 77 .
  • the guide pins 711 are located in the guide holes 742 in a central area.
  • the push member 74 is between the maximum left and maximum right deflection position.
  • damping element 78 is thereby relaxed and can continue to bear against the stop for the damping element 744 at least during part of this state.
  • damping element 78 in the present example a spiral spring, an optional damping element counter-stop 782 is also provided, which limits the maximum compression of the damping element 78 and limits the movement of the thrust member in the direction of the impulse.
  • the cleaning elements are raised in the pushing state via the two levers 921 and the cleaning shafts 92 due to the rotation of the crank element 77 and the resulting movement of the pushing member 74 in the pushing direction.
  • this change in height is exemplified by a comparison of an exemplary height H2 in the overrun state with the height H1 in the initial state.
  • the height of the cleaning elements changes relatively evenly if the drive unit 72 is operated at a constant speed. This is fundamentally desirable since it reduces the wear on the drive unit 72 and also significantly reduces the complexity of the control of the drive unit.
  • the relative potential energy of the cleaning elements increases in the thrust state with the increasing advance of the thrust element 78 in the thrust direction or with the further rotation of the crank element 77.
  • the sensor 75 detects that the thrust member 74 is no longer in the initial state.
  • a positive detection is possible that a cleaning of the biomass heating system is taking place.
  • the figures 20 and 21 show the cleaning device 9 in a maximum stroke state.
  • the thrust member 74 is in the thrust direction, i. H. Viewed from the front in the direction of the left side of the biomass heating system 1, at least largely deflected.
  • the drive unit 72 had moved the thrust member up to a maximum deflection in the thrust direction, until the maximum stroke state of the cleaning device 9 is reached (in 20 the push element is located at maximum on the right, viewed from the front of the biomass heating system 1 at maximum on the left).
  • the guide pins 711 are located in the guide holes 742 of 20 on the left. Accordingly, the lever 922 are now compared to 16 deflected to the respective other side.
  • the damping element 78 is expanded and no longer touches the thrust member 74 .
  • crank element 77 is in a further (second) predetermined crank rotational position (this can also be referred to as the self-running start position), which in 20 is indicated schematically by the dot-dash line extending from the axis of rotation 773 of the crank member 77 to the right.
  • the self-weight of the cleaning elements pushes the pushing member 74 in the direction of the impulse, this force being imparted via the levers of the cleaning shaft 92 .
  • crank element 77 If the crank element 77 now exceeds the predetermined crank rotational position in the maximum stroke state (cf. the dotted line in 20 ), the crank element 77 is no longer pressed in the opposite direction of rotation DR, but is moved in the direction of rotation DR by the push member 74 . This change is defined due to the geometry of the opening 741 and the position of the crank element 77 in relation to the opening 741 .
  • crank element 77 can yield to this pressure or the force exerted and continue to move in the direction of rotation DR independently of the drive unit.
  • the pushing member 74 is pushed in the pushing state until it reaches the maximum stroke state and the self-running start position of the crank member 77 . Thereafter, the pushing member 74 pushes the crank element 77 further in the direction of rotation DR. The falling state, which will be described below, is thus reached.
  • the mechanism of the cleaning device 9 thus begins to run automatically when the self-running start position of the crank element 77 is exceeded, i. i.e. it moves independently of the drive unit 72 in the falling state.
  • a rotational position of the crank element 77 is indicated schematically by the dot-dash line extending upwards from the axis of rotation 773 of the crank element 77 .
  • the crank element 77 sweeps over the rotation range from the self-running starting position or second crank rotation position (in short: second position) to the previously described starting position or first position.
  • the thrust member moves in 22 in the direction of momentum, ie, to the left.
  • the fall state includes a relatively free fall of the cleaning elements, which is only slowed down somewhat by various frictional influences (for example the friction of the cleaning shaft 92 in its bearings or the friction of the turbulators in the boiler tubes 32). A certain moment of inertia of the thrust member 32 also comes into play, but this is just as slight.
  • the magnitude of the acceleration can advantageously be adjusted with the damping element 78, for example with the spring constant of a spiral spring or an oil pressure cylinder, as required by the specific application according to the weight of the cleaning elements and the kinetics of the mechanics of the cleaning device.
  • the acceleration process of the cleaning elements and also of the pushing element 74 in the falling state improves the cleaning effects in the boiler 11 considerably.
  • the various mechanical cleaning effects are also improved due to the resulting increased speed.
  • the impact lever 96 which is also actuated via the cleaning shafts 92, strikes the discharge electrode of the electrostatic precipitator 45 more quickly.
  • a faster movement of the turbulators in the heat exchanger leads to a better effect of breaking up more solid caking or adhesions.
  • the thrust member 74 is again at least largely on the left side of the 22 , and the cleaning elements are again at least approximately at the height of H1 16 and 22 .
  • the thrust member 74 can also strike the damping element counter-stop 782 with its stop 744 . This results in an impact into the boiler 11 and the fall is intercepted.
  • the damping element 78 can also be maximally compressed to end the falling state.
  • a damping element counter-stop 782 is not absolutely necessary.
  • the damping element counter-stop 782 can ensure that a damping element 78 is not subjected to excessive loads and, under certain circumstances, is subjected to excessive wear.
  • the spiral spring could be over-compressed with resulting spring breakage.
  • a cleaning element e.g. the turbulators
  • the cleaning element has a final speed of roughly 1.4 m/s when the stop 744 hits the counter-stop 782.
  • this cleaning element has a weight of 30 kg
  • the cleaning element has a kinetic energy of roughly 29.4 joules at the end of the fall, which is to be evaluated as the energy of a single impact.
  • the entire mechanism of the cleaning device 9 is thus subjected to a strong impact, which can also be released into the boiler 11 via the stops.
  • the cleaning device 9 consequently produces a shaking effect which conventional linearly operating cleaning devices do not produce.
  • the cleaning device 9 described above thus results in an improved cleaning effect, since more solid caking or heavy buildup of combustion residues in the boiler can be detached. If the combustion residues are now better cleaned off, the efficiency of the boiler 11 is improved and the emissions are reduced.
  • the volume of the cleaning is advantageously reduced by the damping element.
  • FIG. 24 discloses another pusher member 74 having an alternative shape the opening 741.
  • the further thrust member 74 is integrated in the same way in the biomass heating system 1, as the thrust member 74 of Figures 13 to 23 . Reference is therefore made to the above explanations, which also with the thrust member 74 of 24 can be realized.
  • the individual states of the thrust member 74 of Figures 13 to 23 correspond to those of 14 .
  • the crank element 771 is located in the 24 in the starting position.
  • the opening 741 has a step 745 on the right side.
  • This step 745 is arranged such that the crank extension 771 or the roller 771 is moved over the step 745 at the end of the pushing state (at the maximum stroke state), and the pushing member 74 is jerked in the impulse direction. An even greater acceleration is thus generated during the transition to the falling state, since the thrust element 74 is not initially pushed against the inertia of the freewheel.
  • the thrust member 74 of 24 advantageously an increased double acceleration, once at the beginning of the fall state and once at the end, which further improves the shaking effect with regard to the impurities.
  • the thrust member 74 also arrives Figures 13 to 23 quite quickly from the maximum lift state to the fall state, since a freewheel, in particular a ball bearing freewheel, can be implemented almost without inertia.
  • the opening 741 is presently provided in an approximately L-shape. However, alternative shapes of the opening 741 are also conceivable.
  • the biomass heating system 1 is preferably designed in such a way that the entire drive mechanism in the lower boiler area (including rotary grate mechanism including rotary grate, heat exchanger cleaning mechanism, drive mechanism for moving floor, mechanism for filter device, cleaning basket and drive shafts and ash discharge screw) can be quickly and efficiently removed and removed again using the "drawer principle”. can be used. This facilitates maintenance work.
  • rotary grate mechanism including rotary grate, heat exchanger cleaning mechanism, drive mechanism for moving floor, mechanism for filter device, cleaning basket and drive shafts and ash discharge screw
  • guide holes 742 are provided with two guide pins 711, only one guide hole 742 with two guide pins 711 may be provided, for example.
  • three guide holes 742 with three guide pins can also be provided.
  • the number of guide holes is not limited to two. The same applies to the peg holes 743.
  • rotary grate elements 252, 253 and 254 instead of only three rotary grate elements 252, 253 and 254, two, four or more rotary grate elements can also be provided. With five rotary grate elements, for example, these could be arranged with the same symmetry and functionality as with the three rotary grate elements presented.
  • the rotary grate elements can also be shaped or designed differently from one another. More rotary grate elements have the advantage that the crushing function is increased.
  • convex sides of the rotary grate elements 252 and 254 concave sides of these can also be provided, in which case the sides of the rotary grate element 253 can be shaped in a complementary convex manner. This is functionally almost equivalent.
  • the rotational flow or turbulent flow in the combustion chamber 24 can be clockwise or counterclockwise.
  • the combustion chamber cover 204 can also be provided with an incline in sections, for example in a stepped manner.
  • the secondary air nozzles 291 are not limited to purely cylindrical bores in the combustion chamber bricks 291 . These can also be designed as frustoconical openings or tapered openings.
  • the secondary (re)circulation can also only be flown with secondary air or fresh air, and in this respect not recirculate the flue gas, but only supply fresh air.
  • Fuels other than wood chips or pellets can also be used as fuels in the biomass heating system.
  • the biomass heating system disclosed here can also be fired exclusively with one type of fuel, for example only with pellets.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Solid-Fuel Combustion (AREA)
EP22213026.2A 2021-03-09 2021-03-09 Dispositif de nettoyage amélioré pour installation de chauffage à biomasse Pending EP4184058A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP22213026.2A EP4184058A1 (fr) 2021-03-09 2021-03-09 Dispositif de nettoyage amélioré pour installation de chauffage à biomasse

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP22213026.2A EP4184058A1 (fr) 2021-03-09 2021-03-09 Dispositif de nettoyage amélioré pour installation de chauffage à biomasse
EP21161524.0A EP4056900B1 (fr) 2021-03-09 2021-03-09 Installation de chauffage à biomasse dotée d'un dispositif amélioré de nettoyage

Related Parent Applications (2)

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EP21161524.0A Division-Into EP4056900B1 (fr) 2021-03-09 2021-03-09 Installation de chauffage à biomasse dotée d'un dispositif amélioré de nettoyage
EP21161524.0A Division EP4056900B1 (fr) 2021-03-09 2021-03-09 Installation de chauffage à biomasse dotée d'un dispositif amélioré de nettoyage

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EP4184058A1 true EP4184058A1 (fr) 2023-05-24

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EP21161524.0A Active EP4056900B1 (fr) 2021-03-09 2021-03-09 Installation de chauffage à biomasse dotée d'un dispositif amélioré de nettoyage
EP22213026.2A Pending EP4184058A1 (fr) 2021-03-09 2021-03-09 Dispositif de nettoyage amélioré pour installation de chauffage à biomasse
EP22708940.6A Pending EP4305352A1 (fr) 2021-03-09 2022-03-01 Système de chauffage de biomasse ayant un dispositif de nettoyage amélioré

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WO (1) WO2022189200A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4375570A1 (fr) * 2022-11-25 2024-05-29 SL-Technik GmbH Installation de chauffage de biomasse à nettoyage amélioré et détection de blocage de celle-ci
CN116878049B (zh) * 2023-06-07 2024-04-09 山西崇光科技有限公司 一种锅炉烟气余热回收热泵的自耦合供热系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2233066A (en) * 1941-02-25 Cleaning device
DE1094912B (de) * 1955-06-15 1960-12-15 William Herbert Smith Vorrichtung zur rauchgasseitigen Reinigung der Rauchrohre stehender Heizkessel
EP1830130A2 (fr) 2006-03-01 2007-09-05 HDG Bavaria GmbH Heizsysteme für Holz Chaudière, en particulier chaudière à combustible solide, dotée d'un volet de gaz de fumée
KR101149359B1 (ko) * 2011-12-05 2012-05-30 (주)규원테크 펠릿 보일러
EP3064276A2 (fr) * 2015-03-04 2016-09-07 Ernst Gerlinger Chaudiere

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2233066A (en) * 1941-02-25 Cleaning device
DE1094912B (de) * 1955-06-15 1960-12-15 William Herbert Smith Vorrichtung zur rauchgasseitigen Reinigung der Rauchrohre stehender Heizkessel
EP1830130A2 (fr) 2006-03-01 2007-09-05 HDG Bavaria GmbH Heizsysteme für Holz Chaudière, en particulier chaudière à combustible solide, dotée d'un volet de gaz de fumée
KR101149359B1 (ko) * 2011-12-05 2012-05-30 (주)규원테크 펠릿 보일러
EP3064276A2 (fr) * 2015-03-04 2016-09-07 Ernst Gerlinger Chaudiere

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WO2022189200A1 (fr) 2022-09-15
EP4305352A1 (fr) 2024-01-17
EP4056900A1 (fr) 2022-09-14
EP4056900B1 (fr) 2023-01-25

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