EP3789672A1 - Installation de chauffage à la biomasse ayant une conduite d'air secondaire, ainsi que ses parties intégrantes - Google Patents

Installation de chauffage à la biomasse ayant une conduite d'air secondaire, ainsi que ses parties intégrantes Download PDF

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Publication number
EP3789672A1
EP3789672A1 EP20194315.6A EP20194315A EP3789672A1 EP 3789672 A1 EP3789672 A1 EP 3789672A1 EP 20194315 A EP20194315 A EP 20194315A EP 3789672 A1 EP3789672 A1 EP 3789672A1
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EP
European Patent Office
Prior art keywords
combustion chamber
combustion
heating system
secondary air
biomass heating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20194315.6A
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German (de)
English (en)
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EP3789672B1 (fr
Inventor
Thilo SOMMERAUER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SL Technik GmbH
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SL Technik GmbH
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Publication date
Priority claimed from EP19195118.5A external-priority patent/EP3789670B1/fr
Application filed by SL Technik GmbH filed Critical SL Technik GmbH
Priority to EP22178909.2A priority Critical patent/EP4086510A1/fr
Publication of EP3789672A1 publication Critical patent/EP3789672A1/fr
Application granted granted Critical
Publication of EP3789672B1 publication Critical patent/EP3789672B1/fr
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    • 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
    • F24H1/0063—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using solid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B30/00—Combustion apparatus with driven means for agitating the burning fuel; Combustion apparatus with driven means for advancing the burning fuel through the combustion chamber
    • 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
    • B03C3/02—Plant or installations having external electricity supply
    • B03C3/04—Plant or installations having external electricity supply dry type
    • B03C3/10—Plant or installations having external electricity supply dry type characterised by presence of electrodes moving during separating action
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B1/00—Combustion apparatus using only lump fuel
    • F23B1/16—Combustion apparatus using only lump fuel the combustion apparatus being modified according to the form of grate or other fuel support
    • F23B1/24—Combustion apparatus using only lump fuel the combustion apparatus being modified according to the form of grate or other fuel support using rotating grate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B10/00—Combustion apparatus characterised by the combination of two or more combustion chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B10/00—Combustion apparatus characterised by the combination of two or more combustion chambers
    • F23B10/02—Combustion apparatus characterised by the combination of two or more combustion chambers including separate secondary combustion chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B30/00—Combustion apparatus with driven means for agitating the burning fuel; Combustion apparatus with driven means for advancing the burning fuel through the combustion chamber
    • F23B30/02—Combustion apparatus with driven means for agitating the burning fuel; Combustion apparatus with driven means for advancing the burning fuel through the combustion chamber with movable, e.g. vibratable, fuel-supporting surfaces; with fuel-supporting surfaces that have movable parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B5/00—Combustion apparatus with arrangements for burning uncombusted material from primary combustion
    • F23B5/04—Combustion apparatus with arrangements for burning uncombusted material from primary combustion in separate combustion chamber; on separate grate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B50/00—Combustion apparatus in which the fuel is fed into or through the combustion zone by gravity, e.g. from a fuel storage situated above the combustion zone
    • F23B50/12—Combustion apparatus in which the fuel is fed into or through the combustion zone by gravity, e.g. from a fuel storage situated above the combustion zone the fuel being fed to the combustion zone by free fall or by sliding along inclined surfaces, e.g. from a conveyor terminating above the fuel bed
    • 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
    • F23B60/02—Combustion apparatus in which the fuel burns essentially without moving with combustion air supplied through a grate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B7/00—Combustion techniques; Other solid-fuel combustion apparatus
    • F23B7/002—Combustion techniques; Other solid-fuel combustion apparatus characterised by gas flow arrangements
    • F23B7/007—Combustion techniques; Other solid-fuel combustion apparatus characterised by gas flow arrangements with fluegas recirculation to combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/24—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having a vertical, substantially cylindrical, combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/24—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having a vertical, substantially cylindrical, combustion chamber
    • F23G5/26—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having a vertical, substantially cylindrical, combustion chamber having rotating bottom
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/10—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of field or garden waste or biomasses
    • F23G7/105—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of field or garden waste or biomasses of wood waste
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23H—GRATES; CLEANING OR RAKING GRATES
    • F23H13/00—Grates not covered by any of groups F23H1/00-F23H11/00
    • F23H13/06—Dumping grates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23H—GRATES; CLEANING OR RAKING GRATES
    • F23H15/00—Cleaning arrangements for grates; Moving fuel along grates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23H—GRATES; CLEANING OR RAKING GRATES
    • F23H9/00—Revolving-grates; Rocking or shaking grates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23H—GRATES; CLEANING OR RAKING GRATES
    • F23H9/00—Revolving-grates; Rocking or shaking grates
    • F23H9/02—Revolving cylindrical grates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J1/00—Removing ash, clinker, or slag from combustion chambers
    • F23J1/02—Apparatus for removing ash, clinker, or slag from ash-pits, e.g. by employing trucks or conveyors, by employing suction devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J15/00—Arrangements of devices for treating smoke or fumes
    • F23J15/02—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material
    • F23J15/022—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material for removing solid particulate material from the gasflow
    • F23J15/025—Arrangements of devices for treating smoke or fumes of purifiers, e.g. for removing noxious material for removing solid particulate material from the gasflow using filters
    • 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
    • F23J3/023—Cleaning furnace tubes; Cleaning flues or chimneys cleaning the fireside of watertubes in boilers
    • 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
    • F23L1/00—Passages or apertures for delivering primary air for combustion 
    • 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
    • F23L3/00—Arrangements of valves or dampers before the fire
    • 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 
    • 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
    • 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
    • F24H1/18—Water-storage heaters
    • F24H1/187—Water-storage heaters using solid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/104—Inspection; Diagnosis; Trial operation
    • 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
    • F24H9/001—Guiding means
    • F24H9/0026—Guiding means in combustion gas channels
    • F24H9/0031—Guiding means in combustion gas channels with means for changing or adapting the path of the flue gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
    • F24H9/2057—Arrangement or mounting of control or safety devices for water heaters using solid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/25—Arrangement or mounting of control or safety devices of remote control devices or control-panels
    • F24H9/28—Arrangement or mounting of control or safety devices of remote control devices or control-panels characterised by the graphical user interface [GUI]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B2700/00—Combustion apparatus for solid fuel
    • F23B2700/018—Combustion apparatus for solid fuel with fume afterburning by staged combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2202/00—Combustion
    • F23G2202/10—Combustion in two or more stages
    • F23G2202/103—Combustion in two or more stages in separate chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2205/00—Waste feed arrangements
    • F23G2205/12—Waste feed arrangements using conveyors
    • F23G2205/121—Screw conveyor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2209/00—Specific waste
    • F23G2209/26—Biowaste
    • F23G2209/261—Woodwaste
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2217/00—Intercepting solids
    • F23J2217/10—Intercepting solids by filters
    • F23J2217/102—Intercepting solids by filters electrostatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2700/00—Ash removal, handling and treatment means; Ash and slag handling in pulverulent fuel furnaces; Ash removal means for incinerators
    • F23J2700/003—Ash removal means for incinerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M2700/00—Constructional details of combustion chambers
    • F23M2700/005—Structures of combustion chambers or smoke ducts
    • F23M2700/0053—Bricks for combustion chamber walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/281—Input from user

Definitions

  • the invention relates to a biomass heating system and its components.
  • the invention relates to a flow-optimized biomass heating system.
  • Biomass heating systems in particular biomass boilers, in a power range from 20 to 500 kW are known. Biomass can be seen as a cheap, domestic, crisis-proof and environmentally friendly fuel. Wood chips or pellets, for example, are available as combustible biomass or as biogenic solid fuels.
  • the pellets mostly consist of wood chips, sawdust, biomass or other materials that have been compacted into small disks or cylinders with a diameter of approx. 3 to 15 mm and a length of 5 to 30 mm.
  • Wood chips also known as wood chips, wood chips or wood chips
  • wood chips is wood that is chopped up 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 an adjoining heat exchange device. Due to the stricter legal regulations in many countries, some biomass heating systems also have a fine dust filter. Various other 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 tank.
  • 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 device for supplying the air in turn normally has a fan with low pressure in order to advantageously influence the thermodynamic factors during the combustion in the combustion chamber.
  • a device for supplying fuel can for example be provided with a side insert (so-called cross-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 furnace grate stores the fuel for the 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 made rigid or movable.
  • grate firing systems in which the combustion air is not fed through the grate, but only from the side.
  • the combustion chamber can also regularly be divided into a primary combustion zone (direct combustion of the fuel on the grate and in the gas space above it before further combustion air is supplied) and a secondary combustion zone (post-combustion zone of the flue gas after another Air supply).
  • the combustion of the pellets or the wood chips essentially has two phases after drying.
  • the fuel is at least partially pyrolytically decomposed and converted into gas by high temperatures and air, which can be blown into the combustion chamber.
  • the (partial) part converted into gas and any remaining solid matter for example charcoal
  • the fuel outgasses, and the resulting gas and the charcoal contained in it 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, whereby the pyrolysis gases can be divided into gases which are condensable at room temperature and gases which are not condensable.
  • Primary pyrolysis takes place at roughly 250-450 ° C and secondary pyrolysis at around 450-600 ° C.
  • the secondary pyrolysis that occurs subsequently is based on the further reaction of the primarily formed pyrolysis products.
  • 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.
  • the gasification can be seen as part of the oxidation; the solid, liquid and gaseous products resulting from the pyrolytic decomposition are brought into reaction by the action of further heat. This is done with the addition of a gasification agent such as air, oxygen, water vapor or even carbon dioxide.
  • a gasification agent such as air, oxygen, water vapor or even carbon dioxide.
  • the lambda value during gasification is greater than zero and less than one.
  • the gasification takes place at around 300 to 850 ° C or even up to 1,200 ° C.
  • Complete oxidation with excess air (lambda greater than 1) then 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 advantageously be regulated by means of a lambda probe provided at the exhaust gas outlet of the boiler.
  • the efficiency of combustion is increased by converting the pellets into gas, because gaseous fuel is better mixed with the combustion air and thus converted more completely, and lower emissions of pollutants, fewer unburned particles and ash (fly ash or dust particles) are generated .
  • exhaust gas recirculation devices In addition to supplying air to the combustion chamber, exhaust gas recirculation devices are also known which recirculate exhaust gas from the boiler to the combustion chamber for cooling and for renewed combustion.
  • Flue gas recirculation can take place under or over the grate.
  • the flue gas recirculation can be mixed with the combustion air or separately.
  • the exhaust from the combustion in the combustion chamber is fed to the heat exchanger so that the hot combustion gases flow through the heat exchanger to transfer heat to a heat exchange medium, which is usually water at around 80 ° C (usually between 70 ° C and 110 ° C ° C).
  • the boiler also usually has a radiation part, which is integrated into the combustion chamber, and a convection part (the heat exchanger connected to it).
  • the ignition device is mostly a hot air device or a glow device.
  • the combustion is started by supplying hot air to the combustion chamber, the hot air being heated by an electrical resistor.
  • the ignition device has a glow plug / glow rod or several glow plugs in order to heat the pellets or the wood chips through direct contact until combustion begins.
  • the glow plugs can also be equipped with a motor in order to remain in contact with the pellets or the wood chips during the ignition phase and then to retract so as not to remain exposed to the flames. This solution is prone to wear and tear and is complex.
  • a disadvantage of conventional biomass heating systems for pellets can be that pellets that fall into the combustion chamber can roll out of the grid or grate or slide off or land next to the grate and can get into 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 lowest chamber of the boiler or the ash shaft. Pellets that do not remain on the grate or grate burn incompletely and thus cause poor efficiency, excessive ash and a certain amount of unburned pollutant particles. This applies to both pellets and wood chips.
  • the known biomass heating systems for pellets in the vicinity of the grid or grate and / or the exit of the combustion gas have, for example, baffles to hold back fuel elements at certain locations.
  • baffles With some boilers, shoulders are provided on the inside of the combustion chamber to prevent pellets from falling into the ash removal and / or the lowest chamber of the boiler.
  • combustion residues can in turn settle, which makes cleaning more difficult and can impede air flows in the combustion chamber, which in turn reduces efficiency.
  • these baffles require their own manufacturing and assembly effort. This applies to both pellets and wood chips.
  • Biomass heating systems for pellets or wood chips have the following further disadvantages and problems.
  • Baffles or shoulders in the combustion chamber can limit this disadvantage and prevent the fuel from rolling or sliding off the grate or even falling into the bottom chamber of the boiler, but they obstruct the air flow and prevent an optimal mixture of air and fuel.
  • Another problem is that incomplete combustion as a result of the non-uniform distribution of the fuel from the grate and as a result of the non-optimal mixture of air and fuel, the accumulation and falling of unburned ash through the air inlet openings, which lead directly to the combustion grate, or from the end of the grate into the air ducts or the air supply area.
  • blower with a low pressure head does not provide a suitable vortex flow of the air in the combustion chamber and therefore does not allow an optimal mixture of air and fuel. In general, it is difficult to develop an optimal vortex flow in conventional combustion chambers.
  • Hot air devices require high electrical power and are expensive. Spark plugs require less electricity, but they require moving parts because the spark plugs must be motorized. They are expensive, complicated, and can be a problem in terms of reliability.
  • the hybrid technology should enable the use of both pellets and wood chips with water contents between 8 and 35 percent by weight.
  • Gaseous emissions 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 above-mentioned task 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 biomass heating system for burning 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 combustion device being the The following comprises: a combustion chamber with a rotating grate, with a primary combustion zone and with a secondary combustion zone; wherein the primary combustion zone is laterally surrounded by a plurality of bricks and from below by the rotating grate; wherein a plurality of secondary air nozzles are provided in the combustion bricks; wherein the primary combustion zone and the secondary combustion zone are separated at the level of the secondary air nozzles; wherein the secondary combustion zone of the combustion chamber is fluidically connected to an inlet of the heat exchanger.
  • a biomass heating system is provided, the secondary air nozzles being arranged in such a way that vortex flows of a flue gas-air mixture of secondary air and combustion air arise around a vertical center axis in the secondary combustion zone of the combustion chamber, the vortex flows to improve the mixing of the flue gas -Air mixture lead.
  • a biomass heating system is provided, the secondary air nozzles in the combustion chamber bricks each being designed as a cylindrical or frustoconical 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 eddy currents, after exiting the combustion chamber nozzle, form spiral rotational currents that extend as far as a combustion chamber ceiling of the combustion chamber.
  • a biomass heating system is provided, the secondary air nozzles in the combustion chamber being arranged at at least approximately the same height; and the secondary air nozzles are arranged with their center axis and / or (depending on the type of nozzle) aligned in such a way that the secondary air is introduced eccentrically to a center of symmetry of the combustion chamber.
  • a biomass heating system is provided, 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 internal diameter of 20 to 35 mm.
  • a biomass heating system wherein 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, the combustion chamber in the secondary combustion zone having a combustion chamber ceiling which is provided inclined upward 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, the inclined combustion chamber 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, 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, the average flow velocity 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 having a modular structure; and in each case two semicircular combustion chamber bricks form a closed ring in order to form the primary combustion zone and / or a part of the secondary combustion zone; and at least two rings are stacked on combustion chamber bricks.
  • a biomass heating system having spiral turbulators arranged in the boiler tubes, which extend over the entire length of the boiler tubes; and the heat exchanger has belt turbulators arranged in the boiler tubes and extending over at least half the length of the boiler tubes.
  • a biomass heating system for burning 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 bundles, wherein the combustion device has the following: a combustion chamber with a rotating grate and with a primary combustion zone and with a secondary combustion zone, preferably provided above the primary combustion zone; wherein the primary combustion zone is laterally surrounded by a plurality of bricks and from below by the rotating grate; wherein the secondary combustion zone includes a combustion chamber nozzle or a burn-through hole; wherein the secondary combustion zone of the combustion chamber is fluidically connected to an inlet or inlet of the heat exchanger; wherein the primary combustion zone has an oval horizontal cross-section.
  • Boiler tubes arranged in bundles can be a plurality of boiler tubes arranged parallel to one another and having 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; d. That is, the inlet openings and the outlet openings of all boiler tubes are at the same height.
  • horizontal can denote a planar alignment of an axis or a cross-section on the assumption that the boiler is also set up horizontally, with which the ground level can be the reference, for example.
  • “horizontal” in the present case can mean “parallel” to the base plane of the boiler 11, as this is usually defined.
  • horizontal can only be understood 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 unhindered vortex flow.
  • 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 ideal "round" cross-section is also possible, but not so well adapted to the geometry of the fuel distribution and also the flow technology of the vortex flow, the asymmetry of the oval compared to the "ideal" circular cross-sectional shape of the combustion chamber an improved formation of a turbulent flow in the combustion chamber enables.
  • a biomass heating system is provided, the horizontal cross-section of the primary combustion zone being provided to be at least approximately constant over a height of at least 100 mm. This also serves for the unimpeded formation of the flow profiles in the combustion chamber.
  • a biomass heating system is provided, the combustion chamber in the secondary combustion zone having a combustion chamber slope which tapers 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 rotating grating element, a second rotating grating element and a third rotating grating element, each around a horizontally arranged bearing axis by at least 90 degrees, preferably at least 160 degrees, more preferably by at least 170 degrees , are rotatably arranged; wherein the rotating grate elements form a combustion surface for the fuel; the rotating grate elements Have openings for the air for combustion, wherein the first rotating grate element and the third rotating grate element are identical in their combustion surface.
  • the openings in the rotating grate elements are preferably slot-shaped and designed in a regular pattern in order to ensure a uniform air flow through the fuel bed.
  • a biomass heating system is provided, the second rotating grate element being positively arranged between the first rotating grating element and the third rotating grating element and having grate lips which are arranged in such a way that they are at least largely sealingly in the horizontal position of all three rotating grating elements on the first rotating grating element and the third rotating grate element.
  • a biomass heating system wherein the rotating grate further has a rotating grate mechanism which is configured such that it can rotate the third rotating grate element independently of the first rotating grate element and the second rotating grate element, and that it can rotate the first rotating grate element and the second rotating grate element can rotate together but independently of the third rotating grate element.
  • a biomass heating system is provided, the combustion surface of the rotating grate elements configuring an essentially oval or elliptical combustion surface.
  • a biomass heating system having mutually complementary and curved sides, the second rotating grating element preferably having concave sides towards the adjacent first and third rotating grating element, and preferably the first and third rotating grating element each towards the second rotating grating element have a convex side.
  • a biomass heating system having a modular structure; and two semicircular combustion chamber bricks each form a closed ring to form the primary combustion zone; and at least two rings are stacked on combustion chamber bricks.
  • a biomass heating system having spiral turbulators arranged in the boiler tubes, which extend over the entire length of the boiler tubes; and the heat exchanger has belt turbulators arranged in the boiler tubes and extending over at least half the length of the boiler tubes.
  • the belt turbulators can preferably be arranged in or within the spiral turbulators.
  • the belt turbulators can be arranged in an integrated manner in the spiral turbulators.
  • the belt turbulators can preferably extend over a length of 30 to 70% of the length of the spiral turbulators.
  • a biomass heating system 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 electrostatic filter device arranged in an integrated manner, which has a spray electrode and a precipitation electrode surrounding the spray electrode and a cage or a cage-shaped cleaning device; wherein the boiler further has a mechanically operable cleaning device with a hammer lever with a stop head; wherein the cleaning device is set up in such a way that it can strike the (spray) electrode at its end with the stop head, so that a shock wave is generated by the electrode and / or a transverse vibration of the (spray) electrode to remove impurities from the electrode to clean up.
  • a steel is provided as the material for the electrode, which can be caused to vibrate (longitudinally and / or transversely and / or shock waves) by the stop head.
  • Spring steel and / or chrome 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 made cambered. The cage-shaped cleaning device can be 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 into the boiler in the cold area being provided, which is configured such that it can clean the boiler tubes of the heat exchanger by moving up and down the turbulators provided in the boiler tubes.
  • the upward and downward movement can also be understood as the back and forth movement of the turbulators in the boiler tubes in the longitudinal direction of the boiler tubes.
  • a biomass heating system with a glow bed height measuring mechanism being arranged in the combustion chamber above the rotating grate; wherein the ember bed height measuring mechanism has a fuel level flap with a main surface which is attached to an axis of rotation; 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 slope for a secondary combustion zone of a combustion chamber of a biomass heating system with the features and properties mentioned herein is disclosed.
  • an electrostatic filter device arranged in an integrated manner for a biomass heating system with the features and properties mentioned herein is disclosed.
  • a glow bed height measurement 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 as such.
  • 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 all possible combinations of features listed together.
  • Expressions such as“ first ",” second “,” primary “or” secondary “as used herein can be used represent different elements regardless of their order and / or meaning and do not restrict corresponding elements.
  • an element e.g., a first element
  • another element e.g., a second element
  • the element may be directly connected to the other element or connected to the other element via another element (e.g. a third element).
  • a term “configured to” (or “arranged”) as used in the present disclosure may be replaced by “suitable for,” “suitable for,” “adapted to”, “made to”, “capable of” or “designed to” depending on what is technically possible.
  • the expression “device configured to” or “set up to” mean that the device can operate in conjunction with another device or component, or can perform a corresponding function.
  • the present individual aspects for example the rotating grate, the combustion chamber or the filter device, are disclosed herein as individual parts or individual devices separately from or separately from the biomass heating system. It is therefore clear to the person skilled in the art that individual aspects or parts of the system are also disclosed here in isolation. In the present case, the individual aspects or parts of the system are disclosed in particular in the sub-chapters identified by brackets. It is envisaged that these individual aspects can also be claimed separately.
  • Fig. 1 shows a three-dimensional overview view 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 system 1
  • the arrow S in the figures indicates the side view of the system 1.
  • the biomass heating system 1 has a boiler 11 which is mounted on a boiler base 12.
  • 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 rotating mechanism holder 22 for a rotating grate 25 (not shown) supports a rotating mechanism 23 with which drive forces can be transmitted to bearing axles 81 of the rotating grate 25.
  • an optional filter device 4 (not shown) with an electrode 44 (not shown) which is suspended by an insulating electrode holder 43 and which is energized via 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 behind the boiler 11, which recirculates part of the exhaust gas via recirculation ducts 51, 53 and 54 and flaps 52 to cool the combustion process and reuse it during the combustion process.
  • the biomass heating system 1 also 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 rotating grate 25.
  • the fuel supply 6 has a rotary valve 61 with a fuel supply opening 65, the rotary valve 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 screw conveyor 67 (not shown) so that the fuel is conveyed in a fuel feed channel 64 to the combustion device 2.
  • an ash removal device 7 which has an ash removal screw 71 in an ash removal channel, which is operated by a motor 72.
  • Fig. 2 now shows a cross-sectional view through the biomass heating system 1 of FIG Fig. 1 which was taken along a section line SL1 and which is shown viewed from the side view S.
  • Fig. 3 which has the same cut as Fig. 2 represents, for the sake of clarity, the flows of the flue gas and flow cross-sections are shown schematically.
  • Fig. 3 It should be noted that individual areas compared to the Fig. 2 are shown dimmed. This is only for the sake of clarity Fig. 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 supplying and removing 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 rotating grate 25, which will be explained in more detail later, on which the fuel bed 28 rests.
  • the multi-part rotating grate 25 is rotatably mounted by means of a plurality of bearing axles 81.
  • the primary combustion zone 26 of the combustion chamber 24 is surrounded by (a plurality of) combustion chamber bricks 29, whereby the combustion chamber 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 essentially oval (for example 380 mm + - 60 mm x 320 mm + - 60 mm; it should be noted that some of the above size combinations can 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 swirl 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 (cf. Fig. 19 ). This creates a vortex or swirling flow S1, which runs upwards in a roughly spiral or helical shape. In other words, an upwardly extending spiral flow 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 bricks 29 thus also protect the other material of the combustion chamber 24, for example cast iron, from the direct action of flames in the combustion chamber 24.
  • the combustion chamber bricks 29 are preferably adapted to the shape of the grate 25.
  • the combustion chamber bricks 29 also have secondary air or recirculation nozzles 291, which recirculate the flue gas into the primary combustion zone 26 for renewed 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 aligned acentrically in order to cause a swirl of the flow in the primary combustion zone 26 (ie a swirl and eddy flow, which will be explained in more detail later).
  • the combustion chamber bricks 29 will be explained in more detail later.
  • An insulation 311 is provided at the boiler tube inlet.
  • 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 vortex 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 level of the combustion chamber nozzles 291 (from a functional or combustion point of view) or at the level of the combustion chamber nozzle 203 (from a purely structural or structural point of view) and defines the radiation part of the combustion chamber 26.
  • the flue gas produced during the 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 Fig. 3 indicated purely by way of example by the arrows S2 and S3.
  • candle-flame-shaped rotary currents S2 appear (cf. also Fig. 21 ), which can advantageously extend up to the combustion chamber ceiling 204, whereby the available space of the combustion chamber 24 is better utilized.
  • the eddy currents are concentrated in the middle of the combustion chamber A2 and make ideal use of the volume of the secondary combustion zone 27.
  • the constriction that the combustion chamber nozzle 203 represents for the eddy currents further reduces the rotational currents, with which turbulence is 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, however, at least partially also retained 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 orientation, they induce eddy currents that set the flue gas / secondary air mixture in rotation and thereby (again in combination with the combustion chamber nozzle 203 improved) enable complete combustion with minimal excess air and thus maximum efficiency. This is also in the Figures 19 to 21 illustrated.
  • 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 burnout speed of the flue gases is accelerated and the completeness of the burnout even with extreme partial load (e.g. 30%) the nominal load) is ensured.
  • the first maintenance opening 21 is insulated with an insulating material, for example 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 configuration of the secondary combustion zone 27 will be explained in more detail later.
  • the flue gas flows into the heat exchange device 3, which has a bundle of boiler tubes 32 provided parallel to one another.
  • the flue gas now flows downwards, as in FIG Fig. 3 indicated by arrows S4.
  • This part of the flow can also be referred to as the convection part, since the heat dissipation of the flue gas essentially takes place on the boiler tube walls via forced convection.
  • the temperature gradients in the heat exchanger medium, for example in the water, caused in the boiler 11 result in a natural convection of the water, which promotes mixing of the boiler water.
  • the exit of the boiler tubes 32 opens into the reversing chamber 35 via the reversing chamber inlet 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 shown in FIG Fig. 2 and 3 shown.
  • the flue gas is introduced back up into the filter device 4 (cf. arrows S5), which in the present case is an electrostatic filter device 4 by way of example.
  • flow diaphragms can be provided at the inlet 44 of the filter device 4, which equalize the flow 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 from 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 spray electrode) inside the electrostatic precipitator.
  • the electrode is preferred with protruding tips and possibly sharp edges, because this is where the density of the field lines and thus also the electrical field strength is greatest and thus the corona discharge is favored.
  • the opposite electrode (collecting electrode) usually consists of a grounded exhaust pipe section which is supported around the electrode.
  • the degree of separation of an electrostatic precipitator depends in particular on the residence 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 generating 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. Fig. 15 ) held approximately in the middle in an approximately chimney-shaped interior of the filter device 4.
  • the electrode 45 consists at least largely of a high-quality spring steel or chromium steel and is held by an electrode holder 43 via a high-voltage insulator, that is to say an electrode insulation 46.
  • the (spray) electrode 45 hangs downward in the interior of the filter device 4 so that it can vibrate.
  • a cage 48 serves at the same time as a counter electrode and as a cleaning mechanism for the filter device 4.
  • the cage 48 is connected to the ground or earth potential. Due to the prevailing potential difference, the exhaust gas flowing in the filter device 4, see arrows S6, is filtered as explained above. In the case of cleaning the filter device 4, the electrode 45 is de-energized.
  • the cage 48 preferably has an octagonal regular cross-sectional profile, as shown, for example, in the view of FIG Fig. 13 can be removed.
  • the cage 48 can preferably be laser cut during manufacture.
  • the flue gas flows through the reversing 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, so that the wall surface facing the heat exchanger 3 and flushed by the heat exchanger medium is also used for heat exchange from the direction of the filter device 4, which further improves the efficiency of the system 1. In this way, at least part of the wall of the filter device 4 can be flushed with the heat exchange medium, whereby at least part of this wall is cooled with boiler water.
  • the cleaned exhaust gas flows out of the filter device 4, as indicated by the arrows S7. After exiting 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 passed out of the boiler 11 via the exhaust gas outlet 41.
  • An ash discharge 7 is arranged in the lower part of the boiler 11.
  • the ash separated and falling out of the boiler 11, for example, from the combustion chamber 24, the boiler tubes 32 and the filter device 4 is conveyed out of the boiler 11 via an ash discharge screw 71.
  • the combustion chamber 24 and the boiler 11 of this embodiment were calculated using CFD simulations. Practical experiments were also carried out to confirm the CFD simulations. The starting point for the considerations was calculations for a 100 kW boiler, although a power range of 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 act multiphase system.
  • CFD simulations are therefore well suited as design and optimization tools.
  • CFD simulations were used in order to optimize the flow 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 significantly defined by the CFD simulation and also by associated practical experiments.
  • the simulation results are based on a flow simulation with consideration of the heat transfer. Examples of the results of such CFD simulations are given in US Pat Fig. 20 and 21 shown.
  • the design of the combustion chamber shape is important in order to be able to meet the requirements of the task.
  • the shape and geometry of the combustion chamber should ensure the best possible turbulent mixing and homogenization of the flow across the cross section of the flue gas duct, a minimization of the combustion volume, as well as a reduction in excess air and the recirculation ratio (efficiency, operating costs), a reduction in CO and CxHx Emissions, NOx emissions, dust emissions, a reduction in local temperature peaks (fouling and slagging) and a reduction in local flue gas speed peaks (material stress and erosion).
  • the Fig. 4 showing a partial view of the Fig. 2 is, and the Fig. 5 , which is a sectional view through the boiler 11 along the vertical section line A2, represent a combustion chamber geometry that meets the aforementioned requirements for biomass heating systems over a wide power range of, for example, 20 to 500 kW is fair.
  • the vertical section line A2 can also be understood as the central or central axis of the oval combustion chamber 24.
  • 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 on the basis of the following basic parameters: A volume with an oval horizontal base with the dimensions of 380 mm + - 60 mm (preferably + -30 mm) x 320 mm + - 60 mm (preferably + -30 mm), and a height of 538 mm + - 80 mm ( preferably + - 50 mm).
  • the above size specifications can also be applied to boilers of other power classes (e.g. 50 kW or 200 kW), scaled in relation to each other.
  • 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 bevel 202 protruding into the secondary combustion zone 27 and which preferably contains the heat exchange medium 38.
  • the combustion chamber bevel 202 reduces the cross section of the secondary combustion zone 27.
  • the combustion chamber bevel 202 is at an angle k of at least 5%, preferably at an angle k of at least 15% and even more preferably at least an angle k of 19% with respect to a fictitious horizontal or straight provided combustion chamber ceiling H (cf. the dashed horizontal line H in Fig. 4 ) intended.
  • a combustion chamber ceiling 204 is also provided inclined in an ascending manner 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 upward in the direction of the inlet 33 of the heat exchanger 3.
  • This combustion chamber ceiling 204 extends in the section of Fig. 2 at least largely straight or straight and inclined.
  • the angle of inclination of the straight or flat combustion chamber ceiling 204 can preferably be 4 to 15 degrees with respect to the (fictitious) horizontal.
  • a further (ceiling) slope is provided in the combustion chamber 24 in front of the inlet 33, which, together with the combustion chamber slope 202, forms a funnel.
  • This funnel turns the upwardly directed swirl or vortex flow to the side and directs this flow roughly into the Horizontal around. 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 flowed evenly, which ensures an evenly distributed flow of the flue gas in all boiler tubes 32. This optimizes the heat transfer in the heat exchanger 3 quite considerably.
  • the combination of the vertical and horizontal slopes 203, 204 in the secondary combustion zone in combination as an inflow geometry in the convective boiler can achieve a uniform distribution of the flue gas over the convective boiler tubes.
  • the combustion chamber bevel 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 results in the most uniform possible distribution of the flue gas to the individual boiler tubes in order to optimize the heat transfer there.
  • the combination of the bevels 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 to 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 in the outer circumference (such a cross-section is shown in FIG Fig. 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 Over the height indicated by the double arrow BK4, the combustion chamber 24 can have an approximately constant cross section.
  • the primary combustion zone 24 can have an approximately oval-cylindrical volume.
  • the side walls and the base (the grate) of the primary combustion zone 26 can preferably be perpendicular to one another.
  • the bevels 203, 204 described above can be provided integrated as walls of the combustion chamber 24, 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 the primary combustion zone 26 of the combustion chamber 24 can also preferably be designed to be regular. Furthermore, the horizontal cross section of the combustion chamber 24 and in particular of the primary combustion zone 26 of the combustion chamber 24 can preferably be a regular (and / or symmetrical) ellipse.
  • the horizontal cross-section (the outer circumference) of the primary combustion zone 26 can be designed to be constant over a predetermined height (for example 20 cm).
  • an oval-cylindrical primary combustion zone 26 of the combustion chamber 24 is provided 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 missing dead spaces also avoid 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 also designed as an oval or approximately circular constriction in order to optimize the flow conditions even further.
  • This optimized nozzle 203 bundles the upwardly rotating flue gas-air mixture and ensures better mixing, preservation of the eddy currents in the secondary combustion zone 27 and thus complete combustion. This also minimizes the excess air required. This improves the combustion process and increases efficiency.
  • a vortex or swirling flow is bundled through the nozzle 203 and directed upwards, so that this flow extends further upwards than is usual in the prior art.
  • this has its cause in the reduction in the swirled distance of the air flow to the rotational or swirl center axis forced by the nozzle 203 (cf. analogously the physics of the pirouette effect).
  • the combustion chamber slope 202 of the Fig. 4 which are also used in the Fig. 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, ensures, according to CFD calculations, an equalization of the flue gas flow in the direction of the heat exchanger device 4, whereby 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 bevel 202, preferably by at least 5%.
  • the combustion chamber bevel 202 is provided on the side of the combustion chamber 25 facing the heat exchange device 4, and is provided rounded at the point of maximum taper.
  • combustion chamber ceiling 204 which runs obliquely upwards to the horizontal in the direction of the inlet 33 and which diverts the eddy currents in the secondary combustion zone 27 to the side, thereby making their flow velocity distribution more uniform.
  • the inflow or deflection of the flue gas flow upstream of the tube bundle heat exchanger is designed in such a way that an uneven inflow of the tubes is avoided in the best possible way, whereby temperature peaks in individual boiler tubes 32 can be kept low and 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 guided through the inclined combustion chamber wall 203 at a uniform speed (also in the case of different combustion states) to the heat exchanger tubes or the boiler tubes 32.
  • This effect is further reinforced by the inclined combustion chamber ceiling 204, a funnel effect being produced.
  • the result is a uniform heat distribution of the individual boiler tubes 32 relating to the heat exchanger surfaces 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 that in the Fig. 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 (among other things due to of flow diaphragms 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 pass minimizes the formation of streaks 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 on the fuel bed 28 in the lower part of the combustion chamber 25. This can cause an initial ignition or a new ignition of the fuel.
  • the ignition device 201 can be a glow igniter be.
  • the ignition device is advantageously arranged in a stationary manner 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 (i.e. after S7) from the filter device.
  • a controller (not shown) can recognize the respective calorific value through the lambda probe.
  • the lambda probe can thus ensure the ideal mixing ratio between the fuels and the oxygen supply. Despite different fuel qualities, a high level of efficiency and a higher degree of efficiency can be achieved as a result.
  • FIG. 5 The fuel bed 28 shown shows a coarse fuel distribution due to the supply of the fuel from the right-hand side of FIG Fig. 5 .
  • a combustion chamber nozzle 203 is shown, in which a secondary combustion zone 27 is provided and which accelerates and bundles the flue gas flow.
  • 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 Fig. 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 rotating grate 25, and in particular of the special design of the combustion chamber bricks 29.
  • the Fig. 7 shows accordingly to Fig. 6 a Exploded view of the combustion chamber bricks 29.
  • the views of the Fig. 6 and 7th can preferably with the dimensions listed above Fig. 4 and 5 be executed. However, this is not necessarily the case.
  • the chamber wall of the primary combustion zone 26 of the combustion chamber 24 is provided with a plurality of combustion chamber bricks 29 in a modular structure, which among other things facilitates manufacture and maintenance. Maintenance is made easier in particular by the possibility of removing individual combustion chamber bricks 29.
  • Form-fitting grooves 261 and projections 262 in order to create a mechanical and largely airtight connection, in order in turn to avoid the ingress of disruptive external air.
  • two at least largely symmetrical combustion chamber bricks each form a complete ring.
  • three rings are preferably stacked on top of one another in order to form the oval-cylindrical or alternatively also at least approximately circular (the latter is not shown) primary combustion zone 26 of the combustion chamber 24.
  • Three further combustion chamber bricks 29 are provided as the upper end, the ring-shaped nozzle 203 being supported by two retaining bricks 264 which are placed onto the upper ring 263 in a form-fitting manner.
  • grooves 261 are provided either for suitable projections 262 and / or for the insertion of suitable sealing material.
  • the retaining stones 264 which are preferably designed symmetrically, can preferably have an inwardly inclined bevel 265 in order to simplify the sweeping of fly ash onto the rotating grate 25.
  • the lower ring 263 of the combustion chamber bricks 29 rests on a base plate 251 of the rotating grate 25. Ash is increasingly deposited on the inner edge between this lower ring 263 of the combustion chamber bricks 29, which thus advantageously seals this transition independently and advantageously when the biomass heating system 1 is in operation.
  • 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 in the combustion chamber bricks 29 at least approximately at the same (horizontal) height as the combustion chamber 24.
  • 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 inner volume of the primary combustion zone 26 of the combustion chamber 24 has an oval horizontal cross-section, which, thanks to an ergonomic shape, avoids dead corners or dead spaces that are usually not optimally flowed through by the flue gas-air mixture, so that the fuel present there is not is burned optimally. Due to the present shape of the combustion chamber bricks 29, the flow of primary air through the grate 25, which also matches the distribution of the fuel over the grate 25, and the possibility of unhindered eddy currents is improved; and consequently, the combustion efficiency 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 inner diameter BK3 and the largest inner diameter BK11. These dimensions were the result of the optimization of the primary combustion zone 26 of the combustion chamber 24 by means of CFD simulation and practical tests.
  • Fig. 8 shows a plan view of the rotating grate 25 from above as seen from the section line A1 of FIG Fig. 2 .
  • the supervision of the Fig. 8 can preferably be designed with the dimensions listed above. However, this is not necessarily the case.
  • the rotating grate 25 has the base plate 251 as a base element.
  • a transition element 255 is provided in a roughly oval-shaped opening of the base plate 251, which bridges a gap between a first rotating grate element 252, a second rotating grating element 253 and a third rotating grating element 254, which are rotatably mounted. So that the rotating grate 25 is provided as a rotating grate with three individual elements, d. In other words, this can also be referred to as a 3-fold rotating grate. Air holes for primary air to flow through are provided in the rotating grate elements 252, 253 and 254.
  • the rotating grate elements 252, 253 and 254 are flat and heat-resistant metal plates, for example made of a cast metal, which have an at least largely flat surface on their upper side and are connected to the bearing axles 81 on their underside, for example via intermediate mounting elements. Viewed from above, the rotating grate elements 252, 253 and 254 have curved and complementary sides or outlines.
  • the rotating grate elements 252, 253, 254 can have mutually complementary and curved sides, the second rotating grating element 253 preferably having concave sides to the adjacent first and third rotating grating elements 252, 254, and preferably the first and third rotating grating elements 252, 254 each has a convex side towards the second rotating grate element 253. This improves the breaker function of the rotating grate elements, since the length of the break is increased and the forces acting to break the break (similar to scissors) attack more specifically.
  • the rotating grate 25 has an oval combustion surface which is more favorable for the fuel distribution, the air flow through the fuel and the burning off of the fuel than a conventional rectangular combustion surface.
  • the combustion surface 258 is essentially formed by the surfaces of the rotating grate elements 252, 253 and 254 (in the horizontal state). The combustion surface is thus the surface of the rotating grate elements 252, 253 and 254 pointing upwards.
  • This oval combustion surface advantageously corresponds to the fuel contact surface when this is applied or pushed onto the side of the rotating grate 25 (see arrow E in FIG Fig. 9 , 10 and 11 ).
  • the fuel can be supplied from a direction which is parallel to a longer central axis (main axis) of the oval combustion surface of the rotating grate 25.
  • the first rotating grate element 252 and the third rotating grate element 254 can preferably be embodied identically in their combustion surface 258. Furthermore, the first rotating grate element 252 and the third rotating grate element 254 can be identical or structurally identical to one another. This is for example in Fig. 9 to see, wherein the first rotating grate element 252 and the third rotating grate element 254 have the same shape.
  • the second rotating grate element 253 is arranged between the first rotating grate element 252 and the third rotating grate element 254.
  • the rotating grate 25 is preferably provided with an approximately point-symmetrical oval combustion surface 258.
  • the rotating grate 25 can also form an approximately elliptical combustion surface 258, DR2 being the dimensions of its main axis and DR1 the dimensions of its minor axis.
  • the rotating grate 25 can have an approximately oval combustion surface 258, which is axially symmetrical with respect to a center axis of the combustion surface 258.
  • the rotating grate 25 can have an approximately circular combustion surface 258, which entails minor disadvantages in terms of fuel supply and distribution.
  • Two motors or drives 231 of the rotating mechanism 23 are also provided, with which the rotating grate elements 252, 253 and 254 can be rotated accordingly. More details on the special function and the advantages of the present rotary grate 25 will be given later with reference to FIG Figures 9 , 10 and 11 described.
  • the ash melting range (this extends from the sintering point to the pouring point) depends to a large extent on the fuel used.
  • Spruce wood for example, has a critical temperature of around 1,200 ° C. But the ash melting range of a fuel can also be subject to strong fluctuations. Depending on the amount and composition of the minerals contained in the wood, the behavior of the ash changes in the combustion process.
  • Another factor that can influence slag formation is the transport and storage of wood pellets or wood chips. This is because these should get into the combustion chamber 24 as undamaged as possible. If the wood pellets have already crumbled when they enter the combustion process, this increases the density of the ember bed. Stronger slag formation is the result. In particular, the transport from the storage room to the combustion chamber 24 is important here. Particularly long distances, as well as bends and angles, lead to damage or abrasion of the wood pellets.
  • the resulting slag (and also the ash) can advantageously be removed due to the special shape and functionality of the rotating grate 25 provided. This is now with respect to the Figures 9 , 10 and 11 explained in more detail.
  • FIGS Fig. 9 , 10 and 11 show a three-dimensional view of the rotating grate 25 with the base plate 251, the first rotating grating element 252, the second rotating grating element 253 and the third rotating grating element 254.
  • the views of FIGS Fig. 9 , 10 and 11 can preferably correspond to the dimensions listed above. However, this is not necessarily the case.
  • This view shows the rotating grate 25 as an isolated insert part with rotating grate mechanism 23 and drive (s) 231.
  • the rotating grate 25 is mechanically provided in such a way that it can be individually prefabricated in the manner of the modular system and inserted as an insert part into a provided elongated opening of the boiler 11 and can be built in. This also makes the maintenance of this wear-prone part easier.
  • the rotating grate 25 can thus preferably be of modular design, it being able to be quickly and efficiently removed and reinserted as a complete part with rotating grate mechanism 23 and drive 231.
  • the modularized rotating grate 25 can thus also be assembled and disassembled by means of quick-release fasteners.
  • the rotating gratings of the prior art are regularly permanently mounted, and thus difficult to maintain or assemble.
  • the drive 231 can have two separately controllable electric motors. These are preferably provided on the side of the rotating grate mechanism 23.
  • the electric motors can have reduction gears. End stop switches can also be provided which provide end stops for the end positions of the rotating grate elements 252, 253 and 254.
  • the individual components of the rotating grate mechanism 23 are provided interchangeably.
  • the gears are provided so that they can be plugged on. This makes maintenance easier and also makes it easier to change sides of the mechanics during assembly, if necessary.
  • the aforementioned openings 256 are provided in the rotating grate elements 252, 253 and 254 of the rotating grate 25.
  • the rotating grate elements 252, 253 and 254 can each be driven by at least 90 degrees, preferably at least 120 degrees, even more preferably by 170 degrees, via their respective bearing axles 81, which are driven by the drive 231, in this case the two motors 231, via the rotary mechanism 23 Degrees are rotated about the respective bearing or axis of rotation 81.
  • the maximum angle of rotation can be 180 degrees, or slightly less than 180 degrees, as permitted by the grate lips 257.
  • the rotary mechanism 23 is set up in such a way that the third rotary grate element 254 can be rotated individually and independently of the first rotary grate element 252 and the second rotary grate element 243, and that the first rotary grate element 252 and the second rotary grate element 243 are rotated together and independently of the third rotary grate element 254 can.
  • the rotating mechanism 23 can be provided accordingly, for example by means of running wheels, toothed or drive belts and / or toothed wheels.
  • the rotating grate elements 252, 253 and 254 can preferably be produced as a cast grate with a laser cut in order to ensure exact dimensional stability. This is in particular in order to define the air guidance through the fuel bed 28 as precisely as possible and to avoid disruptive air flows, for example air streams at the edges of the rotating grate elements 252, 253 and 254.
  • the openings 256 in the rotating grate elements 252, 253 and 254 are set up in such a way that they are small enough for the usual pellet material and / or the usual wood chips that they do not fall through, and that they are large enough that the fuel flows well with air can be.
  • the openings 256 are dimensioned large enough that they can be blocked by ash particles or contaminants (e.g. no stones in the fuel).
  • Fig. 9 now shows the rotating grate 25 in the closed position, with all rotating grate elements 252, 253 and 254 aligned horizontally or closed. This is the position in regular operation. Due to the uniform arrangement of the large number of Openings 256 will ensure a uniform flow through the fuel bed 28 (this is in Fig. 9 not shown) on the rotating grate 25 ensured. In this respect, the optimal combustion state can be established here.
  • the fuel is applied to the rotating grate 25 from the direction of arrow E; in this respect, the fuel is from the right side of the Fig. 9 pushed up onto the rotating grate 25.
  • ash and / or slag collects on the rotating grate 25 and in particular on the rotating grate elements 252, 253 and 254.
  • the rotating grate 25 can be used to efficiently clean the rotating grate 25.
  • Fig. 10 shows the rotating grate in the state of a partial cleaning of the rotating grate 25 in ember preservation mode.
  • the third rotating grate element 254 is rotated. Because only one of the three rotating grate elements is rotated, the embers are retained on the first and second rotating grate elements 252, 253, while at the same time the ash and slag can fall down from the combustion chamber 24. As a result, no external ignition is required to restart operation (this saves up to 90% ignition energy). Another consequence is a reduction in wear on the ignition device (for example an ignition rod) and a saving in electricity. Ash cleaning can also advantageously take place during operation of the biomass heating system 1.
  • Fig. 10 also shows a state of ember preservation during a (often sufficient) partial cleaning.
  • the operation of the system 1 can advantageously take place more continuously, which, in contrast to the usual full cleaning of a conventional grate, does not require a lengthy, complete ignition, which can take several tens of minutes.
  • grate lips 257 (on both sides) of the second rotating grate element 253 can be seen.
  • These grate lips 257 are set up in such a way that the first rotating grate element 252 and the third rotating grate element 254 rest on the upper side of the grate lips 257 when they are closed, and thus the rotating grate elements 252, 253 and 254 are provided without any gaps and are thus provided with a seal.
  • This avoids streams of air and undesirable, uneven primary air flows through the bed of embers. The efficiency of the combustion is thereby advantageously improved.
  • Fig. 11 shows the rotating grate 25 in the state of universal cleaning, which is preferably carried out during a system shutdown. All three rotating grate elements 252, 253 and 254 are rotated, whereby the first and second rotating grate elements 252, 253 are preferably rotated in the opposite direction to the third rotating grate element 254. On the one hand, this realizes a complete emptying of the rotating grate 25, and on the other hand, the ashes and slag now broken up on four odd outer edges. In other words, an advantageous 4-fold breaker function is realized.
  • Fig. 9 What is explained about the geometry of the outer edges also applies in relation to Fig. 10 .
  • the present rotating grate 25 implements normal operation (cf. Fig. 9 ) two different types of cleaning are advantageous (cf. Fig. 10 and 11 ), whereby the partial cleaning allows cleaning while the system 1 is in operation.
  • the present simple mechanical structure of the rotating grate 25 makes it robust, reliable and durable.
  • the heat exchanger 3 has a vertically arranged bundle of boiler tubes 32, with both a spring and a ribbon or spiral turbulator preferably being provided in each boiler tube 32.
  • 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 belt turbulator 37 preferably extends over approximately half the length of the respective boiler tube 32 and has a spiral shape in the axial direction of the Boiler tube 32 extending tape with a material thickness of 1.5 mm to 3 mm. Furthermore, the respective belt turbulator 37 can also be approximately 35% to 65% of the length of the respective boiler tube 32.
  • the respective belt turbulator 37 is preferably arranged with one end at the downstream end of the respective boiler tube 32.
  • the combination of spring and ribbon or spiral turbulator can also be referred to as a double turbulator.
  • Fig. 12 Both ribbon and spiral turbulators are shown.
  • the belt turbulator 37 is arranged inside the spring turbulator 36.
  • Belt turbulators 37 are provided because the belt turbulator 37 increases the turbulence effect in the boiler tube 32 and creates a more homogeneous temperature and speed profile when viewed over the tube cross-section, while the tube without a belt turbulator preferably forms a hot strand with higher speeds in the center of the tube, which extends up to the outlet of the boiler tube 32 continues, which would have a negative effect on the efficiency of the heat transfer.
  • the belt turbulators 37 thus improve the convective heat transfer in the lower region of the boiler tubes 32.
  • 22 boiler tubes with a diameter of 76.1 mm and 3.6 mm wall thickness can be used, for example.
  • the pressure loss in this case can be less than 25 Pa.
  • the spring turbulator 36 ideally has an outside diameter of 65 mm, a pitch of 50 mm, and a profile of 10 ⁇ 3 mm.
  • the belt turbulator 37 can have an outside diameter of 43 mm, a pitch of 150 mm and a profile of 43 ⁇ 2 mm.
  • a sheet metal thickness of the belt turbulator can be 2 mm.
  • boiler tubes 32 with a diameter between 60 and 80 mm and a wall thickness of 2 to 5 mm can be used to achieve sufficient efficiency.
  • the pressure loss can be between 20 and 40 Pa and is therefore to be assessed as positive.
  • the outer diameter, the pitch and the profile of the spring and belt turbulators 36, 37 are provided in a correspondingly adapted manner.
  • the desired target temperature at the outlet of the boiler tubes 32 can preferably be between 100 and 160 degrees Celsius at nominal output.
  • Fig. 13 shows a cleaning device 9, with which both the heat exchanger 3 and the filter device 4 can be cleaned automatically.
  • the Fig. 13 shows the cleaning device from the boiler 11 for the sake of clarity.
  • the cleaning device 9 affects the entire boiler 11 and thus affects 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 two cleaning drives 91, preferably electric motors, which rotatably drive two cleaning shafts 92, which in turn are mounted in a shaft holder 93.
  • the cleaning shafts 92 can preferably also be rotatably supported at a further location, for example at the distal ends.
  • the cleaning shafts 92 have extensions 94 to which the cage 48 of the filter device 4 and turbulator holders 95 are connected via joints or rotary bearings.
  • the turbulator bracket 95 is in Fig. 14 highlighted and shown enlarged.
  • the turbulator holder 95 is designed like a comb and is preferably designed to be horizontally symmetrical.
  • the turbulator holder 95 is also a flat piece of metal with a material thickness in the thickness direction D between 2 and 5 mm educated.
  • the turbulator holder 95 has two pivot bearing receptacles 951 on its underside for connection to pivot bearing journals (not shown) of the extensions 94 of the cleaning shafts 92.
  • the pivot bearing receptacles 951 have a horizontal play in which pivot bearing journals or a pivot bearing linkage 955 can / can move back and forth.
  • Vertically protruding extensions 952 have a plurality of recesses 954 in and with which the double turbulators 36, 37 can be attached.
  • the recesses 954 can have a spacing from one another which corresponds to the aisle spacing 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 hinder 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 a receptacle rod) and is thus fixed and secured. This makes assembly much easier.
  • the Figures 15 and 16 show the cleaning mechanism 9 without the cage 48 in two different states.
  • the cage holder 481 can be seen better.
  • Fig. 15 shows the cleaning mechanism 9 in a first state, with both the turbulator holders 95 and the cage holder 481 being in a lower position.
  • a two-armed hammer 96 with a stop head 97 is attached to one of the cleaning shafts 92.
  • the hammer 96 can alternatively also be provided with one or more arms.
  • the hammer 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 it.
  • Fig. 16 shows the cleaning mechanism 9 in a second state, both the turbulator holders 95 and the cage holder 481 being in an upper position.
  • both the turbulator holder 95 and the cage holder 481 are raised vertically via the extensions 952 (and a pivot linkage 955) by rotating the cleaning shafts 92 by means of the cleaning drives 91.
  • the double turbulators 36, 37 in the boiler tubes 32 and also the cage 48 in the chimney of the filter device 4 can thus be moved up and down and can clean the respective walls of fly ash or the like accordingly.
  • the hammer 96 with the stop head 97 can also strike the end of the (spray) electrode 45 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 these the electrode is moved on its suspension) that the (spray) electrode 45 according to its vibration characteristics after the excitation the impact itself can swing (ideally freely).
  • the type of stop determines the vibrations or vibration modes of the (spray) electrode 45.
  • the (spray) electrode 45 can be struck from below (ie from its longitudinal axis direction or from its longitudinal direction) to excite a shock wave or a longitudinal vibration become.
  • the (spray) electrode 45 can also be placed on the side (in the Figures 15 and 16 for example from the direction of the arrow V), so that this oscillates transversely. Or the (spray) electrode 45 (as in the present case in FIGS Figures 15 and 16 shown) at the end of which are hinged from below from a slightly laterally offset direction. In the latter case, a plurality of different types of vibration are generated in the (spray) electrode 45 (by striking), which advantageously add up in the cleaning effect and improve the cleaning efficiency. In particular, the shear action of the transverse vibration on the surface of the (spray) electrode 45 can improve the cleaning effect.
  • a shock 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 oscillation of the (Spray) electrode 45 due to the acting transverse forces (which are oriented 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 oscillation of the electrode 45 can once again lead to improved cleaning of the electrode 45.
  • the cleaning device 9 is simple and inexpensive to manufacture in the manner described and has a simple and low-wear structure.
  • the cleaning device 9 with the drive mechanism is set up in such a way that ash residues can advantageously already be cleaned off by the turbulators from the first pull of the boiler tubes 32 and can fall downwards.
  • 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 disadvantageously increases wear and tear.
  • the electrodes of the filter device 4 can advantageously also be cleaned during operation or during operation of the boiler 11.
  • the biomass heating system 1 is preferably designed in such a way that the complete drive mechanism in the lower boiler area (including rotating grate mechanics including rotating grate, heat exchanger cleaning mechanism, drive mechanism for push floor, mechanism for filter device, cleaning basket and drive shafts and ash removal screw) can be quickly and efficiently removed and restored using the "drawer principle" can be used.
  • rotating grate mechanics including rotating grate, heat exchanger cleaning mechanism, drive mechanism for push floor, mechanism for filter device, cleaning basket and drive shafts and ash removal screw
  • FIG. 17 shows an (exposed) ember bed height measuring mechanism 86 with a fuel level flap 83.
  • FIG. 8 shows a detailed view of the fuel level flap 83 of FIG Fig. 17 .
  • the ember bed height measuring mechanism 86 has in detail an axis of rotation 82 for the fuel level flap 83.
  • the axis of rotation 82 has a central axis 832 and on one side has a bearing notch 84 for holding the axis of rotation 82, as well as a sensor flange 85 for fastening an angle or rotation sensor (not shown).
  • the axis of rotation 82 is preferably provided with a hexagonal profile.
  • the holder of the fuel level flap 83 can be provided in such a way that it consists of two openings 834 with a hexagon socket.
  • the fuel level flap 83 can thus be simply plugged onto the axis of rotation 82 and fixed.
  • the fuel level flap 83 can be a simple sheet metal part.
  • the ember bed height measuring mechanism 86 is provided in the combustion chamber 24, preferably slightly offset to the center, above the fuel bed 28 or the combustion surface 258 so that the fuel level flap 83 is raised depending on the fuel that may be present depending on the height of the fuel or fuel bed 28 , whereby the axis of rotation 82 is rotated in dependence on the height of the fuel bed 28.
  • This rotation or also the absolute angle of the axis of rotation 82 can be detected by a non-contact rotation and / or angle sensor (not shown). This means that an efficient and robust ember bed height measurement can be carried out in the present case.
  • the fuel level flap 83 is set up in such a way that it is chamfered in relation to the center axis 823 of the axis of rotation 82.
  • a surface parallel 835 of a main surface 831 of the fuel level flap 83 can be arranged in such a way that it is provided at an angle with respect to the center axis 823 of the axis of rotation 82. This angle can preferably be between 10 and 45 degrees.
  • the surface parallel 835 and the central axis 823 are conceived in such a way that they (projected in the horizontal plane) can intersect in the central axis 823 to form angles.
  • the surface parallel 835 is normally not aligned parallel to the leading edge of the fuel level flap 83.
  • the fuel level flap 83 the exact height of the ember bed can be determined by means of a contactless rotation and / or angle sensor even in spite of different or varying fuel (wood chips, pellets).
  • the ergonomically sloping shape adapts ideally to the fuel, which is also introduced at an angle by the stoker worm, and ensures representative readings.
  • the fuel height (and quantity) remaining on the combustion surface 258 of the rotating grate 25 can also be precisely determined, with which the fuel supply and the flow through the fuel bed 28 can be regulated in such a way that the combustion process can be optimized.
  • FIG. 13 shows a horizontal cross-sectional view through the combustion chamber at the level of the secondary air nozzles 291 and along the horizontal section line A6 of FIG Fig. 5 .
  • a length of a secondary air nozzle 291 can be between 40 and 60 mm, for example.
  • a (maximum) diameter of the cylindrical or frustoconical secondary air nozzle 291 can be between 20 and 25 mm, for example.
  • the angle shown relates to the two secondary air nozzles 291 closest to the longer main axis of the oval.
  • the angle which is specified as 26.1 degrees by way of example, is measured between the center axis of the secondary air nozzle 291 and the longer of the main axes of the oval of the combustion chamber 24.
  • the angle can preferably in a range of 15 degrees to 35 degrees.
  • the remaining secondary air nozzles 291 can furthermore be provided with an angle of their center axis which functionally corresponds to that of the two secondary air nozzles 291 closest to the longer main axis of the oval for causing the vortex flow (for example with respect to the combustion chamber wall 24).
  • Fig. 19 10 secondary air nozzles 291 are shown, which are arranged in such a way that their central axis or orientation, which is shown with the respective dashed (central) lines, is provided acentric to the (symmetry) center of the oval of the combustion chamber geometry.
  • the secondary air nozzles 291 are not aimed at the center of the oval combustion chamber 24, but at its center or center axis (in Fig. 4 marked A2) over.
  • the center axis A2 can accordingly also be understood as an axis of symmetry relating to the oval combustion chamber geometry 24.
  • the secondary air nozzles 291 are aligned in such a way that they introduce the secondary air tangentially into the combustion chamber 24 when viewed in the horizontal plane.
  • the secondary air nozzles 291 are each provided as an inlet for the secondary air that is not oriented towards the center of the combustion chamber.
  • such a tangential inlet can also be used with a circular combustion chamber geometry.
  • All secondary air nozzles 291 are aligned in such a way that they each cause either a clockwise or counterclockwise flow. In this respect, each secondary air nozzle 291 can contribute to the creation of the eddy currents, with each secondary air nozzle 291 having a similar orientation. It should be noted above that in exceptional cases individual secondary air nozzles 291 can also be arranged neutrally (with alignment in the middle) or in opposite directions (with opposite alignment), although this can worsen the fluidic efficiency of the arrangement.
  • Fig. 20 shows three horizontal cross-sectional views for different boiler dimensions (50 kW, 100 kW and 200 kW) through the combustion chamber 24 of FIG Fig. 2 and 4th at the level of the secondary air nozzles 291 with information on the flow distributions in this cross-section in the respective nominal load case.
  • FIG Fig. 20 For clarification, the relevant flow velocities of these nozzle flows are explicitly shown in FIG Fig. 20 specified. It can be seen here that the resulting nozzle flows extend relatively far into the combustion chamber 24, with the result that strong eddy currents can be produced which cover a large part of the volume of the combustion chamber 24.
  • the arrow in the combustion chamber 24 of the CFD calculation for a 200 kW boiler dimensioning indicates the swirl or vortex direction of the vortex flows induced by the secondary air nozzles 291. This also applies to the other two boiler dimensions (50 kW, 100 kW) of the Fig. 20 .
  • a clockwise vortex flow (viewed from above) is given as an example.
  • Secondary air (preferably simply ambient air) is introduced into the combustion chamber 24 via the secondary air nozzles 291.
  • the secondary air in the secondary air nozzles is accelerated to more than 10 m / s in the nozzle when the load is high.
  • the penetration depth of the resulting air jets in the combustion chamber 24 is increased, which is sufficient to induce an effective vortex flow which extends over the majority of the combustion chamber volume extends.
  • Fig. 21 shows three vertical cross-sectional views for different boiler dimensions (50 kW, 100 kW and 200 kW) through the biomass heating system along the section line SL1 of Fig. 1 with information on the tangential entry of the secondary nozzle flows into this cross-section.
  • Fig. 21 roughly indicate the same gray tones areas with the same flow velocity.
  • candle-flame-shaped rotational flows S2 (cf. also Fig. 3 ) are present, which can advantageously extend to the combustion chamber ceiling 204.
  • the boiler tubes 32 are flowed through quite evenly in the direction of the inlet 33 at approximately 1-2 m / s due to the funnel explained above.
  • rotating grate elements 252, 253 and 254 instead of just three rotating grate elements 252, 253 and 254, two, four or more rotating grate elements can also be provided. With five rotating grate elements, for example, these could be arranged with the same symmetry and functionality as the three rotating grate elements presented.
  • the rotating grate elements can also be shaped or designed differently from one another. More rotating grate elements have the advantage that the crusher function is reinforced.
  • the rotational flow or vortex flow in the combustion chamber 24 can be provided clockwise or counterclockwise.
  • the combustion chamber ceiling 204 can also be provided inclined 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 waisted openings.
  • the secondary (re) circulation can also only have secondary air or fresh air flowing through it, 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 for the biomass heating system.
  • the presently disclosed biomass heating system 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)
  • Environmental & Geological Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Biomedical Technology (AREA)
  • Human Computer Interaction (AREA)
  • Health & Medical Sciences (AREA)
  • Wood Science & Technology (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Solid-Fuel Combustion (AREA)
  • Chimneys And Flues (AREA)
  • Gasification And Melting Of Waste (AREA)
  • Processing Of Solid Wastes (AREA)
EP20194315.6A 2019-09-03 2020-09-03 Installation de chauffage à la biomasse ayant une conduite d'air secondaire, ainsi que ses parties intégrantes Active EP3789672B1 (fr)

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EP19210080.8A EP3789671B1 (fr) 2019-09-03 2019-11-19 Installation de chauffage à biomasse à système de recirculation à traitement optimisé des gaz de fumée
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CN114909655A (zh) * 2022-05-18 2022-08-16 许耀华 一种降低氮氧化物的分级挪热燃烧方法
CN115405917A (zh) * 2022-08-29 2022-11-29 中国石油工程建设有限公司 烟气再循环无氮燃烧耦合二氧化碳捕集工艺系统及方法
CN115899805A (zh) * 2022-11-23 2023-04-04 浙江萨弘科技有限公司 一种电采暖炉
EP4332436A1 (fr) * 2022-09-01 2024-03-06 SL-Technik GmbH Installation de chauffage à biomasse dotée d'un dispositif de filtre électrostatique amélioré
EP4521021A1 (fr) * 2023-09-08 2025-03-12 Fröling Heizkessel- und Behälterbau Ges.m.b.H. Chaudière à biomasse et procédé de fonctionnement d'une chaudière à biomasse

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EP3892918A1 (fr) 2019-09-03 2021-10-13 SL-Technik GmbH Dispositif de nettoyage pour une grille rotative d'une installation de chauffage à biomasse, procédé de nettoyage de la grille

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CN114484573A (zh) * 2021-12-18 2022-05-13 嘉寓光能科技(阜新)有限公司 生物质民用多功能智能化采暖炉
CN114484573B (zh) * 2021-12-18 2023-08-29 嘉寓光能科技(阜新)有限公司 生物质民用多功能智能化采暖炉
CN114909655A (zh) * 2022-05-18 2022-08-16 许耀华 一种降低氮氧化物的分级挪热燃烧方法
CN115405917A (zh) * 2022-08-29 2022-11-29 中国石油工程建设有限公司 烟气再循环无氮燃烧耦合二氧化碳捕集工艺系统及方法
EP4332436A1 (fr) * 2022-09-01 2024-03-06 SL-Technik GmbH Installation de chauffage à biomasse dotée d'un dispositif de filtre électrostatique amélioré
CN115899805A (zh) * 2022-11-23 2023-04-04 浙江萨弘科技有限公司 一种电采暖炉
EP4521021A1 (fr) * 2023-09-08 2025-03-12 Fröling Heizkessel- und Behälterbau Ges.m.b.H. Chaudière à biomasse et procédé de fonctionnement d'une chaudière à biomasse

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EP3789672B1 (fr) 2022-06-29
CN114729748A (zh) 2022-07-08
CA3152396A1 (fr) 2021-03-11
CN114729748B (zh) 2023-05-12
CA3152400C (fr) 2022-11-01
JP7196365B2 (ja) 2022-12-26
US20220341625A1 (en) 2022-10-27
AU2020342698A1 (en) 2022-04-07
US20220333770A1 (en) 2022-10-20
JP2022537844A (ja) 2022-08-30
CN114729744A (zh) 2022-07-08
US20220333822A1 (en) 2022-10-20
CN114729743B (zh) 2023-04-11
CA3152397A1 (fr) 2021-03-11
AU2020342698B2 (en) 2022-06-30
US20220333817A1 (en) 2022-10-20
CN114729747A (zh) 2022-07-08
EP4086510A1 (fr) 2022-11-09
JP2022536880A (ja) 2022-08-19
CN114729747B (zh) 2023-04-21
US11635231B2 (en) 2023-04-25
CN114729743A (zh) 2022-07-08
US11708999B2 (en) 2023-07-25
CA3152394A1 (fr) 2021-03-11
JP7233614B2 (ja) 2023-03-06
AU2020342700A1 (en) 2022-04-21
AU2020342700B2 (en) 2022-07-28
CA3152400A1 (fr) 2021-03-11
CA3152397C (fr) 2022-11-29
CA3152396C (fr) 2022-11-29
CA3152394C (fr) 2022-11-22

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