EP0233330B1 - Ensemble de brûleur-chaudière - Google Patents

Ensemble de brûleur-chaudière Download PDF

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Publication number
EP0233330B1
EP0233330B1 EP86115977A EP86115977A EP0233330B1 EP 0233330 B1 EP0233330 B1 EP 0233330B1 EP 86115977 A EP86115977 A EP 86115977A EP 86115977 A EP86115977 A EP 86115977A EP 0233330 B1 EP0233330 B1 EP 0233330B1
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EP
European Patent Office
Prior art keywords
burner
mixing device
air
combustion chamber
set forth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86115977A
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German (de)
English (en)
Other versions
EP0233330A1 (fr
Inventor
Elmar Goller
Heinrich Prof. Dr.-Ing. Eickhoff
Albrecht Dipl.-Ing. Kayser
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.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
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Publication of EP0233330A1 publication Critical patent/EP0233330A1/fr
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Publication of EP0233330B1 publication Critical patent/EP0233330B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C6/00—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion
    • F23C6/04—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection
    • F23C6/045—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection with staged combustion in a single enclosure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/005—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space with combinations of different spraying or vaporising means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/106—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet
    • F23D11/107—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet at least one of both being subjected to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/402—Mixing chambers downstream of the nozzle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/34—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air
    • F23D14/36—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air in which the compressor and burner form a single unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/02—Liquid fuel
    • F23K5/14—Details thereof
    • F23K5/142—Fuel pumps
    • F23K5/145—Fuel pumps combined with fans
    • 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
    • F23M5/00—Casings; Linings; Walls
    • F23M5/08—Cooling thereof; Tube walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/025—Regulating fuel supply conjointly with air supply using electrical or electromechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/285—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with the fire tubes arranged alongside the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/11101—Pulverising gas flow impinging on fuel from pre-filming surface, e.g. lip atomizers

Definitions

  • the invention relates to an oil burner boiler unit according to the preamble of claim 1.
  • the atomizing device is designed as a flat cutting edge, which generates a flat mixture jet, the flame of which is stabilized in the combustion chamber by deflection on a baffle plate.
  • This known unit is able on the one hand to process particularly small amounts of oil with low pollutants and cover a wide control range of the heating power, but on the other hand it tends to deposit oil coke if the air pressure is too low. It has also proven difficult to ignite the flame with a high voltage arc.
  • a known burner-boiler unit, from which the preamble of claim 1 is based, is described in WO 8 504 947.
  • the combustion chamber is divided into two parts separated by a turbulator.
  • a conventional oil or gas burner creates a flame in the first part of the combustion chamber, whereby the combustion gases can be given a certain rotation.
  • the first part of the combustion chamber is traversed by flue gas pipes, through which the flue gas flows out of the second part of the combustion chamber.
  • the second part of the combustion chamber is surrounded by a heat exchanger. Because cooling takes place in the second part of the combustion chamber, sufficient combustion of the carbon monoxide to carbon dioxide is not guaranteed.
  • the heating output can only be varied within a relatively small control range depending on the heating requirements of the connected consumer.
  • the object of the invention is to create an oil burner / boiler unit in which the heating power can be varied within a wide control range and which enables low-pollutant combustion without the formation of oil coke.
  • the combustion air is supplied at a relatively high pressure, namely proportionally to the oil.
  • the pressure at which the air is supplied is preferably between 20 and 200 mbar.
  • This high pressure means turning away from the fan wheels usually used, in which the vast majority of the drive energy is lost.
  • the swirling mixture flow entering the combustion chamber generates a flame-stabilizing recirculation of hot flue gases without the risk of residue deposits and also allows the combustion to be ignited by an electric arc in the central or external return flow area.
  • hot combustion chamber walls in the front area of the combustion chamber can be dispensed with.
  • the water cooling of the jacket in the first part of the combustion chamber (primary zone) lowers the gas temperature, which in conjunction with the short dwell time of the gas in the highly loaded primary zone results in a reduction in nitrogen oxide formation.
  • the remaining reaction temperature is maintained by the heat-insulating jacket in order to ensure the combustion of the carbon monoxide CO to carbon dioxide CO 2 .
  • the fuel pressure source can consist of a compressed gas line when using gas as fuel. If liquid fuel is used, the fuel source contains a feed pump, preferably a positive displacement pump, which is driven synchronously with a positive displacement pump contained in the compressed air source. An annular constriction can be provided between the two parts of the combustion chamber, which supports recirculation in the primary zone and mixing in the secondary zone.
  • the flow path of the flue gases in the heat exchanger is so narrow that a turbulent flow occurs in this flow path at least in the upper speed range of the drive.
  • the heat transfer coefficient increases significantly more with increasing flow than with laminar-flow heat exchangers, i.e. the heat exchanger requires a smaller increase in its heat exchange surfaces with increasing heating capacity.
  • the gas outlet temperature rises less with high heating output.
  • a fixed heat exchanger can be used in the entire output range of the burner with minor changes in the flue gas temperature.
  • a control range of heating power of about 1: 2.5 can be with a fixed airflow nozzle in the Mixing device to be worked.
  • the cross section of the swirl nozzle is changed as a function of the heating power, and preferably as a function of the pressure of the compressed air source. The greater this air pressure, the larger the flow cross section is made at the swirl nozzle. In this way, the swirl nozzle is matched to the heating power required in each case.
  • the control range of the heating output can be increased up to about 1:10.
  • the invention is also suitable for a burner-boiler unit with gas operation. While the swirl-producing mixing device is used both for atomizing the heating oil as well as for mixture formation and flame stabilization during oil operation, the atomizing effect does not apply to a gas burner. The advantages of pollutant reduction and the speed-dependent fuel-air compound control are retained.
  • the two combustion pumps are expediently combined to form a single structural unit, the housing of this structural unit being divided by an intermediate wall which is penetrated by an intermediate shaft connecting the rotors of the two positive displacement pumps.
  • the composite positive displacement fan means more work than the radial fans commonly used with gas fan burners, but this is more than offset by various savings even with a non-power-controlled single-stage burner.
  • volumetric gas metering depends only slightly on the gas pressure in the gas network, so that no pressure regulator is required.
  • a pressure switch is also not required, as the control only fails if the compound fan fails. In such a case, safety devices switch off the gas supply simply because there is no combustion air or the power supply. It is particularly advantageous that speed control is only required for the drive motor of the composite displacement fan and that complex mixing devices with volume control are not required.
  • the fittings and lines between the solenoid valve and the mixing device remain filled with residual gas each time it is switched off, which then seeps into the combustion chamber.
  • the infiltration of residual gas into the combustion chamber can be avoided by placing a small check valve between the inlets of the air blower and gas blower. As soon as the gas supply is shut off, the gas blower sucks in air via the check valve in order to purge the residual gas from the lines. Even if the power supply network fails, the after-running of the drive motor causes the gas to be flushed out of the gas line.
  • the controllable burner-boiler unit shown in FIG. 1 has an electric motor 10, the speed of which is controlled by a speed control unit 11.
  • the output shaft of the electric motor 10 drives a compressed air displacement pump 12 and a heating oil displacement pump 13.
  • the two pumps 12 and 13 are positive displacement pumps, i.e. their delivery rate is proportional to the drive speed. Roots pumps, gear pumps or piston pumps are suitable for this.
  • the pressure lines of the two displacement pumps 12 and 13 lead to the mixing device 14 designed as an atomizing device.
  • the mixing device 14 is accommodated in the nozzle housing 15, which at the same time forms the end of the combustion chamber 16.
  • the tubular nozzle housing 15 has a cover wall 17 closing the combustion chamber 16 on the combustion chamber side and is sealed at the opposite (outer) end with a cover 18.
  • An oil supply line 19 designed as a capillary line is sealingly passed through the cover 18.
  • the oil supply line 19 leads through the nozzle body 20 arranged in the interior of the nozzle housing 15 and exits at its end face.
  • numerous swirl-generating air-conducting elements in the form of vanes 23 are arranged on the flange-like end wall 22 of the nozzle body. These wings 23 are inclined in the circumferential direction according to FIG. 2 and they taper towards the inner end.
  • the vanes 23 delimit channels 24 through which the radially inflowing air receives a peripheral component.
  • Each of the channels 24 is reduced in cross-section to its inner end, so that the air in each channel 24 increasingly be is accelerated.
  • the wings 23 are arranged between the end wall 22 and a plate 25 running parallel to this end wall.
  • the end wall of the plate 25 facing away from the vanes 23 forms the boundary wall of a further swirl nozzle with vanes 26 which are attached to the end side of a further plate 27.
  • the plate 27 runs parallel to the plate 25 and its wings 26 are designed and arranged in the same way as the wings 23 of the plate 22.
  • the air flowing laterally into the nozzle housing 15 through the inlet 28 is distributed in the interior of the nozzle housing and flows radially into the channels 24 between the vanes 23 and into the corresponding channels between the vanes 26.
  • the wings 23 and 26 give the air a twist, i.e. a circular motion.
  • the plate 25 has an annular shape and its inner edge has the shape of an annular cutting edge 29 projecting axially in the flow direction and tapering towards the end.
  • the inner edge of the annular plate 27 is also bent axially in the flow direction and forms a conical ring 30. which surrounds the cutting edge 29 at a radial distance.
  • the heating oil emerging through the tube 21 is caught by the rotating air stream and sprayed onto the inside of the cutting edge 29.
  • the cutting edge 29 is surrounded on both sides by rotating and axially moving air currents, which tear off the heating oil film from the circular sharp tip of the cutting edge 29 and distribute it finely and evenly.
  • the fuel oil droplets mix intimately with the combustion air and together with this enter the tubular combustion chamber 16.
  • ring-shaped flow rollers arise in the front part 16a of the combustion chamber 16, in which part of the mixture flow is returned and which rotate around the longitudinal axis.
  • an electrode 31 is arranged in part 16a of the combustion chamber.
  • Another electrode 31 ' is used for flame monitoring. After ignition, a stable blue flame arises in part 16a of the combustion chamber 16, which essentially fills the part 16a entirely and continues into the rear part 16b.
  • the part 16a forms the primary combustion zone, which is separated from the part 16b by a ring 32, which forms a constricting constriction 33.
  • the peripheral wall of a part 16b, which forms the secondary combustion zone, is provided with a heat-insulating lining 34 and thereby protected against cooling by the heat exchanger.
  • the heat exchanger 35 surrounds the combustion chamber 16 in a ring shape.
  • the path of the water which is supplied to the heat exchanger 35 is shown in solid lines in FIG. 1, while the path of the combustion gases is shown in dashed lines.
  • the water flows axially from the inlet 36 through the outer annular space 37 until it is deflected at the end of this outer annular space 37 on the burner side and reaches the central annular cavity 38.
  • the water flows through this in countercurrent to the cavity 37.
  • the end of the central cavity 38 facing away from the atomizing and mixing device 14 is connected via bent pipe pieces 39 to the inner annular cavity 40 which is flowed through in the opposite direction to the central cavity 38.
  • the outlet 41 for the heated water is arranged near the nozzle-side end of the central cavity 40.
  • the inner boundary wall of the inner cavity 40 is formed by the tube 42, which represents the wall of the combustion chamber 16.
  • the outer wall of the inner cavity 40 consists of the tube 43.
  • the middle cavity 38 is delimited by the tubes 44 and 45 and the outer cavity 37 by the tubes 46 and 47. All tubes 42 to 47 are arranged coaxially with one another and surround them Combustion chamber 16.
  • the collection chamber 48 adjoins the part 16b of the combustion chamber 16, through which the combustion gases enter the annular gap 49 between the tubes 43 and 44.
  • the annular gap 49 is flowed through in the opposite direction to the combustion chamber 16.
  • the fuel gases are then redirected again in order to get into the annular space 50 between the tubes 45 and 46.
  • the outlet end of the annular space 50 is located at the end of the heat exchanger 35 facing away from the mixing device 14. From there, the combustion gases enter the outlet 51, which is separated from the collecting chamber 48 by a heat-insulated wall 52, into a chimney.
  • the swirling mixture flow entering the combustion chamber 16 generates in the first part 16a, which is water-cooled through the wall 42, both a central and a peripheral heating gas recirculation, which stabilize the blue, low-emission heating oil flame.
  • the second part 16b mainly carbon monoxide CO still contained in the heating gas burns to carbon dioxide CO 2 .
  • the part 16b is protected against further cooling by the heat-insulating lining 34. After leaving the secondary combustion zone, to which the deflection space 48 also belongs, the fuel gas has largely reacted.
  • the annular spaces 49 and 50 have a relatively small radial width, so that turbulence can be generated by wall friction. Such turbulence occurs in particular when the motor 10 runs at the upper speed range and delivers a large amount of air at high heating power. Since the heat transfer of the heat exchanger is improved by a turbulent flow, the heat exchanger output adapts to a certain extent to the heating output of the burner.
  • Fig. 3 shows a variant to change the flow cross section of the mixing device for changing the swirl component.
  • the wings 23 are not rigidly attached to the end wall 22, but each wing 23 is pivotally mounted on the central plate 25 on an axis 55.
  • Pins 56 protrude from the upper plate 22, each of which projects into an elongated hole 57 of a wing 23.
  • the middle plate 25 is rotatably supported, and by rotating this plate 25, the angle of attack of the wings mounted on it can be changed in the manner shown in FIG. 3.
  • the plate 25 is rotated by a rod 58 which is connected to the periphery of the plate 25 via a joint 59.
  • the rod 58 protrudes through a tube 60 into a housing 61 which has a ventilation opening 62.
  • the housing 61 there is a bellows 63, which is sealingly connected to the end of the tube 60.
  • the pressure prevailing in the interior of the nozzle housing 15 passes through the pipe 60 into the interior of the bellows 63. The greater this pressure, the further the rod 58 is drawn into the housing 61.
  • the bellows 63 also acts as a spring, which strives to push the rod 58 out of the housing 61. Due to the rod 58 acting tangentially on the plate 25, the plate 25 is rotated as a function of the pressure prevailing in the nozzle housing 15, as a result of which the vanes 23 are pivoted about their axes 55. The greater the pressure in the nozzle housing 15, the greater the cross section of the channels 24 defined by the vanes 23, i.e. the more the tip of a wing 23 is moved away from the adjacent wing.
  • FIG. 4 also shows a swirl nozzle 53 pressed into sheet metal.
  • the heating oil pipe 21 described above can also be replaced by a spray nozzle 70 which is connected to the feed line 19.
  • the air supplied through the inlet 28 flows between fixed vanes 71 which, like the vanes 23 and 26 of the first embodiment, are inclined to impart a peripheral component to the air flowing radially inwards.
  • the wings 71 are partially covered on their upper side by a plate 72 which leaves an outer edge slot 73 through which the air can pass between the wings 71.
  • the outer edge of the annular cutting edge 29 is fastened to the inner ends of the wings 71, in fact halfway up these wings, so that the cutting edge 29 is swept by the rotating air flow both on its underside and on its upper side.
  • the wings 71 rest on the end wall 17 of the combustion chamber. This end wall also carries the electrodes 31 for igniting the flame.
  • the spray emerging from the spray nozzle 70 is sprayed onto the inside of the annular blade 29 and entrained by the rotating air flow.
  • the resulting fine oil film on the blade 29 is carried along by the two air currents at the tear-off edge of the blade and is introduced into the combustion chamber 16 as a rotating spray cone.
  • FIG. 5 is largely the same as that of FIG. 4, but there is no separate spray nozzle. Rather, the feed line 19 leads into the interior of the edge region of the blade 29. Here there is an annular cavity 64 which is connected to the inside of the blade 29 via micro-slots 75. The oil passes through the annular space 64 to the inside of the blade 29 and is entrained here by the rotating and axially moving air stream.
  • Fig. 6 The embodiment of Fig. 6 is similar to that of Fig. 4, except for the fact that there is no cutting edge.
  • the spray nozzle works as a swirl pressure nozzle with air support by the air flowing between the vanes 71.
  • the mixing and atomizing device 14 of FIG. 7 largely corresponds to that of FIG. 1.
  • the tube 21 projects through an opening in the end wall 22 and behind this there is the plate 25 with the annular conical cutting edge 29. Behind the plate 25 is the Plate 27 is arranged with the likewise annular conical cutting edge 29a, which forms an annular gap with the cutting edge 29.
  • the package consisting of the end wall 22 and the plates 25 and 27 contains tangential bores 80 which lead from the nozzle housing 15 into the swirl nozzle 14.
  • the bores 80 are located in the end wall 22 or the plate 25, so that the air flowing from these bores into the nozzle rotates along the inside of the cutting edge 29.
  • the bores 81 are located on the underside of the plate 25 or the top of the plate 27, so that the air flowing through these bores 81 flows along the outside of the cutting edge 29 in a rotating manner. Both air currents have the same direction of rotation.
  • FIG. 8 shows a gas burner / boiler unit, only the primary combustion zone 16a of the combustion chamber being shown, which is delimited by the ring 32, which forms the constriction constriction 33.
  • the burner is essentially constructed in the same way as the oil burners described above, so that the differences from the oil burners are mainly explained below.
  • the mixing device 14 consists of the swirl nozzle 53 which has inclined vanes 71 for the combustion air and an axial nozzle opening 29 behind it.
  • the inner ends of the wings 71 are delimited by the underside of the conical cover member 85.
  • Above the cover member 85 is the guide ring 86, which is designed as an inner cone and, together with the cover member 85, forms a conical passage which leads from the axial bore 88 to the outer regions of the vanes 71.
  • the gas supply line 87 the outlet of which is in the Middle of the underside of the cover member 85 is located so that the fuel gas axially enters the swirl nozzle 53, while the air enters radially and receives a tangential component through the wing 71.
  • the double displacement blower 89 consists of the air displacement pump 12 and the fuel gas displacement pump 13.
  • the displacement blower 89 is mounted on the nozzle housing 15 and supplies the combustion air via the bore 88 and the fuel gas to the mixing device 14 via the gas supply line 87.
  • the displacement pumps 12 and 13 consist of gear pumps in the present case. These pumps are shown in a section which runs in the central plane between the two pump gears, so that only the cogwheel 90 and 91 which is running and is not driven from the outside can be seen.
  • the axes of the pump gearwheels run at right angles to the longitudinal axis of the swirl nozzle 53.
  • the pump gearwheel 90 of the air displacement pump is mounted in the wall 92 and the intermediate wall 93 of the pump housing, and the pump gearwheel 91 of the gas displacement pump 13 is located in the intermediate wall 93 and the housing wall 96 stored.
  • the axes of the indirectly driven pump gears 90 and 91 run on a common line, just as the axes of the directly driven pump gears (also not shown) also run on a common line. It is also possible to produce both pump gear wheels 90, 91 from a single block, which is only supported in the walls 92 and 93 or 92 and 96. In the same way, the directly driven pump gears can consist of a common block that is only supported in two walls.
  • the air displacement pump 12 draws the combustion air from the outside via a silencer 97 and the inlet pipe 98.
  • a collecting chamber 99 is located between the displacer blower 12 and the bore 88.
  • the fuel gas is pressed out of the gas line via a filter 100 and two solenoid valves 101 into the suction chamber 102 and conveyed into the collecting chamber 103 by the displacing fan 13.
  • the gas line 87 leads from the collecting space 103 to the mixing device 14. As long as the line gas pressure is higher than the combustion chamber pressure, the gas pressure drives the displacement pump 13, which thus works as a motor, which partially relieves the electric motor driving the two displacement pumps 12 and 13.
  • check valve 104 Between the air inlet 98 and the suction chamber 102 there is a check valve 104, which can let air through from the air inlet 98 to the suction chamber 102, but which cannot let gas through in the opposite direction.
  • the check valve 104 is kept closed by the gas pressure as long as the solenoid valves 101 are open. When the gas is shut off, the check valve opens due to the suction effect of the displacement fan 13, so that air is sucked into the displacement fan 13 and at the same time residual gas is flushed out of the gas displacement fan 13 and the gas line 87 and still burns in the combustion chamber.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Combustion Of Fluid Fuel (AREA)

Claims (9)

1. Ensemble de brûleur-chaudière de chauffage comprenant un dispositif de mélange (14) disposé à une extrémité d'une chambre de combustion tubulaire (16), une source de pression de combustible et une source d'air comprimé (12) qui sont raccordées à ce dispositif de mélange (14), et un échangeur de chaleur (35) entourant la chambre de combustion (16), cette chambre de combustion (16) étant formée d'une partie (16a) située du côté du dispositif de mélange (14) et d'une partie (16b) située du côté opposé à ce dispositif de mélange (14), tandis qu'un étranglement (33) est prévu entre ces deux parties (16a et 16b) et que la partie (16a) de la chambre de combustion (16) située du côté du dispositif de mélange (14) comporte une enveloppe refroidie par l'eau de l'échangeur de chaleur (35), caractérisé en ce que la pression de la source d'air comprimé (12) est supérieure à environ 15 mbars et en ce que la partie (16b) de la chambre de combustion (16) située du côté opposé au dispositif de mélange (14) est séparée de l'échangeur de chaleur (35) par une enveloppe d'isolation thermique (34).
2. Ensemble de brûleur-chaudière de chauffage suivant la revendication 1, caractérisé en ce qu'une pompe d'alimentation (13) formant la source de pression de combustible et la source d'air comprimé (12) sont constituées par des pompes volumétriques qui sont entraînées en synchronisme par un dispositif moteur commun à vitesse de rotation réglable (10).
3. Ensemble de brûleur-chaudière de chauffage suivant la revendication 2, caractérisé en ce que le trajet d'écoulement des gaz de combustion dans l'échangeur de chaleur (35) est si étroit que, au moins dans le domaine supérieur des vitesses de rotation du dispositif moteur (10), il se présente un écoulement turbulent dans ce trajet d'écoulement (49, 50).
4. Ensemble de brûleur-chaudière de chauffage suivant l'une des revendications 1 à 3, caractérisé en ce que le dispositif de mélange (14) comprend une buse à impulsion de rotation (53).
5. Ensemble de brûleur-chaudière de chauffage suivant la revendication 4 pour du fioule en tant que combustible, caractérisé en ce que le dispositif de mélange (14) est un dispositif de pulvérisation qui comprend une lame biseautée annulaire conique (29), en ce qu'il est prévu un dispositif d'application permettant une répartition uniforme du fioule sur une surface de la lame biseautée (29) et en ce que des éléments de guidage d'air conduisent l'air amené, en lui impartissant une impulsion de rotation, sur au moins l'une des deux surfaces de la lame biseautée et le long de celle-ci.
6. Ensemble de brûleur-chaudière de chauffage suivant la revendication 5, caractérisé en ce que les éléments de guidage d'air sont des ailettes (23, 26) dont chacune peut pivoter autour d'un axe (55) de façon telle que la distance de sa pointe à l'ailette voisine varie.
7. Ensemble de brûleur-chaudière de chauffage suivant la revendication 6, caractérisé en ce que la commande des ailettes (23, 26) s'effectue à l'aide d'un organe pneumatique de réglage (58, 63) en fonction de la pression d'alimentation du dispositif de mélange (14).
8. Ensemble de brûleur-chaudière de chauffage suivant l'une des revendications 2 à 7, caractérisé en ce que les deux pompes volumétriques (12, 13) sont réunies en une pompe double qui comprend deux paires de rotors reliés rigidement entre eux, chaque paire de rotors, un de chaque pompe, étant disposée avec leurs axes le long d'une droite commune.
9. Ensemble de brûleur-chaudière de chauffage suivant l'une des revendications précédentes pour du gaz en tant que combustible, caractérisé en ce qu'une tuyauterie d'air (98) conduisant à la pompe volumétrique d'air (12) est reliée, par l'intermédiaire d'un clapet antiretour (104), à une tuyauterie de gaz conduisant à la pompe volumétrique des gaz (13), ce clapet antiretour s'ouvrant de la tuyauterie d'air (98) vers la tuyauterie de gaz.
EP86115977A 1986-01-18 1986-11-18 Ensemble de brûleur-chaudière Expired EP0233330B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3601343 1986-01-18
DE3601343 1986-01-18
DE19863608698 DE3608698A1 (de) 1986-01-18 1986-03-15 Brenner-heizkessel-einheit
DE3608698 1986-03-15

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EP0233330A1 EP0233330A1 (fr) 1987-08-26
EP0233330B1 true EP0233330B1 (fr) 1989-04-05

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WO1992000490A1 (fr) * 1990-06-29 1992-01-09 Nippon Chemical Plant Consultant Co., Ltd. Bruleur
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DE4216532C2 (de) * 1992-05-19 1997-02-20 Webasto Thermosysteme Gmbh Niederdruckluftstrom-Zerstäuber für flüssigen Brennstoff eines Brenners
AT410588B (de) * 1998-11-12 2003-06-25 Windhager Zentralheizung Ag Kessel für flüssige brennstoffe
DE10121144A1 (de) * 2001-04-30 2002-11-07 Webasto Thermosysteme Gmbh Heizgerät mit einem Sekundärbrennbereich
DE10144407B4 (de) * 2001-09-10 2007-05-10 Webasto Ag Düse zum Zerstäuben von flüssigem Brennstoff
DE10144408B4 (de) * 2001-09-10 2007-05-10 Webasto Ag Düse zum Zerstäuben von flüssigem Brennstoff
DE10205573B4 (de) * 2002-02-11 2005-10-06 J. Eberspächer GmbH & Co. KG Zerstäuberdüse für einen Brenner
DE10211590B4 (de) * 2002-03-15 2007-11-08 J. Eberspächer GmbH & Co. KG Zerstäuberdüse, insbesondere für ein Fahrzeugheizgerät
DE10331575B4 (de) * 2003-07-11 2005-08-25 Webasto Ag Brenner für ein Heizgerät mit einer Brennstoffdüse
DE102004029029B4 (de) * 2004-06-09 2018-12-13 Deutsches Zentrum für Luft- und Raumfahrt e.V. Einspritzkopf
EA008046B1 (ru) * 2005-02-22 2007-02-27 Александр Владимирович Клюев Способ сжигания топлива (варианты) и установка для его осуществления (варианты)
DE102005022772A1 (de) * 2005-05-12 2007-01-11 Universität Karlsruhe Brenner mit Teilvormischung und -vorverdampfung des flüssigen Brennstoffs
DE102008026478A1 (de) * 2008-06-03 2009-12-10 Deutz Ag Heizeinrichtung für ein Gebäude
JP6542659B2 (ja) * 2015-12-25 2019-07-10 リンナイ株式会社 燃焼装置
CN112443964B (zh) * 2019-08-28 2022-09-13 青岛经济技术开发区海尔热水器有限公司 燃气热水器及其控制方法

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DE3608698C2 (fr) 1990-05-03
EP0233330A1 (fr) 1987-08-26
DE3608698A1 (de) 1987-07-23

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