EP3462088A1 - Dispositif de mélange d'air/gaz de combustion et appareil de chauffage - Google Patents

Dispositif de mélange d'air/gaz de combustion et appareil de chauffage Download PDF

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Publication number
EP3462088A1
EP3462088A1 EP18197115.1A EP18197115A EP3462088A1 EP 3462088 A1 EP3462088 A1 EP 3462088A1 EP 18197115 A EP18197115 A EP 18197115A EP 3462088 A1 EP3462088 A1 EP 3462088A1
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EP
European Patent Office
Prior art keywords
fuel
venturi tube
air
mixing device
air mixing
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
EP18197115.1A
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German (de)
English (en)
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EP3462088B1 (fr
Inventor
Alvaro Carlos Catalan Barriuso
Patrick Glaser
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3462088A1 publication Critical patent/EP3462088A1/fr
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Publication of EP3462088B1 publication Critical patent/EP3462088B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • 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
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • F23D14/64—Mixing devices; Mixing tubes with injectors

Definitions

  • the invention relates to a fuel-air mixing device, in particular for a fan assisted heater, comprising an air inlet, an outer Venturi tube with a first Engestelle, an inner Venturi tube with a second constriction and a nozzle in the region of the second throat for supplying fuel ,
  • the invention also relates to a heater with a fuel-air mixing device according to the present invention.
  • the DE102016201624A1 shows and describes a fuel-air mixing device in the form of a venturi for a blower-assisted burner.
  • the air intake takes place through the blower, the injection of the gaseous fuel into the air flow is arranged in front of the blower. Due to the negative pressure conditions in the area of the constriction of the Venturi, the gaseous fuel is sucked in there automatically.
  • Heaters with such an arrangement have the advantage that the power over a particularly large range (> 1:10) can be varied. In order to minimize the power consumption, today's demands on the modulation width of the power increasingly larger venturi lengths are necessary.
  • a fuel-air mixing device in particular for a fan assisted heater, is disclosed.
  • the fuel-air mixing device comprises an air inlet, an outer Venturi tube with a first Engestelle, an inner Venturi tube with a second constriction and a nozzle in the region of the second bottleneck for supplying fuel.
  • the fuel-air mixing device is characterized in that the inner Venturi tube is disposed within the outer Venturi tube.
  • a "Venturi tube” is to be understood as meaning a tube which has a minimal cross-sectional area in a constriction. Starting from the constriction, the venturi widens in the direction of an exit opening of the venturi tube. The cross-sectional area increases from the constriction, starting in the direction of the outlet opening. Advantageously, the venturi widens starting from the constriction in the direction of an inlet opening. Advantageously, the cross-sectional area of the bottleneck increases starting in the direction of the outlet opening. Preferably, the cross-sectional area of the Venturi tube is circular or substantially circular.
  • cross-sectional area of the Venturi tube is also conceivable, in particular oval and / or elliptical and / or rectangular and / or polygonal.
  • the "cross-sectional area” is to be understood as meaning the cross-sectional area of the air-carrying or gas-conducting part of the venturi tube, in particular of the fuel-air mixture.
  • the Venturi tube related features with the proposed adjective "first” in the present description relate to the outer Venturi tube.
  • the venturi-related features with the proposed adjective “second” in the present description refer to the inner venturi tube.
  • a “first bottleneck” is a bottleneck of the outer Venturi tube.
  • a “first outlet opening” is an outlet opening of the outer venturi tube.
  • a “first inlet” is an inlet of the outer venturi.
  • a second A “second exit port” is an exit port of the inner venturi tube, and a “second entry port” is an entry port of the inner venturi tube.
  • a "blower assisted heater” means a heater in which a burner is primarily powered by a blower with air for combustion.
  • a preferred gaseous fuel is introduced into an airflow conveyed by the fan or mixed in by a fuel-air mixing device, so that a fuel-air mixture is supplied to the burner. The air is sucked in by the blower.
  • a burner supported by the fan should be used to distinguish atmospheric burners where the burner uses the free ambient air for combustion. Examples of atmospheric burners are Bunsen burners or gas radiant heaters or gas infrared radiators.
  • the outer venturi tube has a first outlet opening
  • the inner venturi tube has a second outlet opening and if the second outlet opening is arranged largely at the first constriction of the outer venturi tube, this has the advantage that the fuel-air mixture flowing out of the inner venturi tube adjoins one Point minimum pressure in the outer Venturi tube flows. In this way, the pressure difference between the second constriction of the inner venturi and the first outlet opening of the outer venturi becomes particularly large. This allows the construction of a particularly compact fuel-air mixing device.
  • the second outlet opening is arranged largely at the first constriction
  • a distance of the second outlet opening with respect to a longitudinal direction of the fuel-air mixing device to the first constriction is less than 10% of a venturi length of the outer Venturi tube, preferably less than 4%, more preferably less than 1%.
  • the longitudinal direction of the fuel-air mixing device is arranged parallel to a longitudinal axis or axis of symmetry of the fuel-air mixing device and shows from the first inlet opening or from the air inlet to the first outlet opening.
  • the longitudinal direction is largely in the direction of the flowing into the fuel-air mixing device air flow and the outflowing fuel-air mixture.
  • the distance of the second outlet opening to the first constriction with respect to the longitudinal direction is measured between a first plane which lies in the second outlet opening and a second plane which lies in the first constriction, along the longitudinal direction.
  • the first plane lies on an outermost edge of the inner venturi, which is located on the side of the second outlet opening.
  • the outer edge forms the second outlet opening.
  • the second plane intersects the outer venturi so that a corresponding cross-sectional area is minimal.
  • the "venturi length" is the distance of the first constriction to the first outlet opening along the longitudinal direction.
  • the nozzle is arranged substantially concentrically within the inner Venturi tube, the resulting fuel-air mixture flows largely laminar. In this way, a particularly high pressure recovery by the fuel-air mixing device is made possible. A less symmetrical arrangement of the nozzle can lead to turbulences, which cause a pressure drop.
  • substantially concentric is to be understood that an axis of symmetry of the nozzle is arranged substantially parallel to an axis of symmetry of the inner Venturi tube and the distance of the axis of symmetry of the nozzle to the axis of symmetry of the inner Venturi tube is less than 10% of Venturi diameter of the inner Venturi tube, preferably less than 4%, more preferably less than 1%.
  • the inner Venturi tube arranged largely concentrically within the outer Venturi tube, a laminar flowing fuel-air mixture is even better possible.
  • substantially concentric is to be understood that the axis of symmetry of the inner venturi tube to a Symmetryeachse the outer venturi tube or to the axis of symmetry of the fuel-air mixing device is arranged substantially parallel and the distance of the axis of symmetry of the inner Venturi tube to the axis of symmetry of the outer Venturi tube less than 10% of Venturi diameter of the outer Venturi tube, preferably less than 4%, particularly preferably less than 1%.
  • a possible laminar flowing fuel-air mixture can be ensured if the inner Venturi tube and / or the outer Venturi tube each have a substantially circular cross-section. In this way, the symmetry of the fuel-air mixing device is further increased.
  • the term "cross-section" is intended to mean the shape of the cross-sectional area of the air-carrying or gas-conducting part of the venturi, in particular of the fuel-air mixture
  • the laminarity of the inflowing air can be improved.
  • the first inlet opening is arranged largely at the second inlet opening is to be understood that a distance of the first inlet opening with respect to the longitudinal direction of the fuel-air mixing device to the second inlet opening is less than 10% of the venturi length of the outer Venturi tube, preferably smaller than 4%, more preferably less than 1%.
  • the distance of the first inlet opening to the second inlet opening with respect to the longitudinal direction is measured between a third plane which lies in the first inlet opening and a fourth plane which lies in the second inlet opening, along the longitudinal direction.
  • the third plane lies on an outermost edge of the outer venturi, which is located on the side of the first inlet opening.
  • the fourth level is located on an outermost edge of the inner venturi, which is located on the side of the second inlet opening.
  • a “throttle” is understood to mean a component which causes a pressure drop in a gas flowing through and / or passing by.
  • a throttle may be a plate introduced perpendicular to the flow direction of the fuel.
  • a throttle reduces a flow cross-section of the gas or fluid.
  • adjustable throttle should be understood a throttle in which the pressure drop is adjustable.
  • An “exchangeable fixed throttle” is an interchangeable, attachable to the nozzle component, which causes a predetermined pressure drop of the fuel. It is envisaged that different interchangeable fixed throttles each having different predetermined pressure drops can be attached to the nozzle, in particular for adaptation of the nozzle or the fuel-air mixing device to different types of fuel.
  • a heater with a burner assisted by a fan and a fuel-air mixing device according to the present invention which supplies in particular a gaseous fuel via a fuel line sucked through the air flow through a fuel line
  • a fuel-air mixing device offers more options as to where and with which orientation the fuel-air mixing device can be installed in the heater. This allows a particularly safe and / or reliable construction of the heater. Furthermore, access to components of the heating system during maintenance and / or inspection can be improved in this way.
  • the blower of the fuel-air mixing device provides air with an adjustable air flow, this is the burner output very reliable adjustable.
  • adjustable airflow is meant an adjustable volume airflow.
  • the air flow can be adjusted via a fan with a variable fan speed and / or variable fan power.
  • a fuel regulating valve provides the fuel with a predeterminable, in particular constant, pressure
  • this has the advantage that in this way the fuel / air ratio can be set particularly reliably.
  • it is possible to set the fuel-air ratio constant to a predetermined value.
  • the pressure of the fuel can be regulated to the ambient pressure or to an ambient pressure with an offset.
  • the fuel control valve may be a pneumatic control valve, in particular a zero pressure regulator. In this way, the fuel control valve can react very quickly to changes in ambient pressure and allow a largely constant fuel-air ratio.
  • FIG. 1 schematically components of a heater 10 are shown.
  • the heater 10 includes other components, not shown, such as a heat exchanger, pumps, or an exhaust system.
  • the type and number of components depends on the equipment level of the heater.
  • FIG. 1 1 shows a fuel-air mixing device 12, a blower 14, a burner 16, a fuel valve 18, an ionisation probe 20 and a control unit 22.
  • the burner 16 has a flame 24.
  • the ionisation probe 20 protrudes into the flame 24.
  • the blower 14 is intended to suck in air 26.
  • a blower speed of the blower 14 is variably adjustable.
  • the fuel-air mixing device 12 is provided to mix the intake air 26 with a fuel 28 to a fuel-air mixture 30.
  • the fuel 28 is passed through a fuel line 32 through the fuel valve 16 and then into the fuel-air mixing device 12.
  • the fuel valve 16 is provided to provide the fuel 28 at a predeterminable pressure.
  • the fuel valve 16 is designed in the embodiment as a pneumatic zero pressure regulator.
  • the fuel 28 is provided to the fuel-air mixing device 12 at a pressure substantially equal to the ambient pressure.
  • the fuel 28 is provided at a pressure that is substantially equal to the ambient pressure minus or plus an offset.
  • the fuel 28 is connected to the Fuel valve 18 is set to a fixed predetermined pressure. It is also conceivable that the pressure of the fuel 28 is variable as needed, for example, depending on operating conditions and / or external conditions.
  • the fuel valve 16 may be an electrically adjustable valve, which is adjustable by the control unit 22.
  • the pressure of the fuel 28 may be adjustable, for example, as a function of an operating mode of the heater 10, of a fuel type determined by the control unit 22, and / or of a desired heating power.
  • the blower 14 is intended to direct the fuel-air mixture 30 or a fuel-air mixture stream 30 into the burner 16.
  • the control unit 22 is connected via bus lines 34 to the components of the heater 10, in particular to the blower 14 and the ionization probe 20.
  • the control unit 22 is intended to control an air flow 26 of the intake air 26, in particular the control unit 22 is intended to to adjust the blower speed of the blower 14.
  • the set fan speed of the blower 14 or the set air flow 26, which is conveyed by the blower, depends in particular on a requested heating power of the heating system 10.
  • the control unit 22 is provided in the exemplary embodiment to receive measured values from the ionization probe 20.
  • the ionization probe 20 measures an ionization current of the flames 24.
  • the ionization current makes it possible to draw conclusions about the combustion taking place at the burner 16. For example, from the ionization current conclusions on a quality of the combustion possible, in particular on a fuel-air ratio of the fuel-air mixture 30, or on a quality and / or type or variety of the fuel 28. In particular, with the help of the ionization probe 20 detectable if a flame 24 is present.
  • control unit 22 may be provided to control the heating system as a function of the ionization current.
  • control unit 22 to control an electronic fuel valve 18 to adjust the fuel-air ratio in dependence on the ionisationsstrom. This may be necessary, for example, if the fuel type and / or fuel quality changes.
  • FIG. 2 shows a detailed view of the fuel-air mixing device 12 of the embodiment.
  • the fuel-air mixer 12 includes an outer venturi 36 and an inner venturi 38.
  • the inner venturi 38 is disposed within the outer venturi 36.
  • the outer venturi 36 has a first constriction 40.
  • the inner venturi 38 has a second constriction 42.
  • the outer venturi tube 36 has a first outlet opening 44.
  • the inner venturi 38 has a second outlet opening 46.
  • the first exit opening 44 is provided to discharge a fuel-air mixture 30 from the outer venturi 36.
  • the second exit port 46 is provided to discharge a fuel-air mixture 30 from the inner venturi 38.
  • the outer venturi 36 has a first inlet opening 48.
  • the inner venturi 38 has a second inlet opening 50.
  • the first inlet 48 is intended to introduce air 26 into the outer venturi 36.
  • the second inlet 50 is intended to introduce air 26 into the inner venturi 38.
  • the first inlet opening 48 and the second inlet opening 50 form an air inlet 52 of the fuel-air mixing device 12.
  • the fuel-air mixing device 12 has a nozzle 54.
  • the nozzle 12 is connected to the fuel line 32.
  • the nozzle 54 is provided to inject fuel 28 into the fuel-air mixing device 12 initiate.
  • the nozzle 54 is arranged in the region of the second constriction 42.
  • the second outlet opening 46 is arranged in the region of the first constriction 40.
  • the fuel-air mixing device 12 is constructed in the exemplary embodiment cylindrically symmetric or rotationally symmetrical.
  • the essential, in FIG. 2 The outer venturi tube 36 and the inner venturi tube 38 are substantially rotationally symmetrical with respect to the longitudinal axis 55.
  • a longitudinal direction 57 is disposed parallel to the longitudinal axis 55 and points in the direction of the in the fuel-air mixing device 12 sucked in air stream 26 and in the direction of the flowing out of the fuel-air mixing device 12 Brenstoff-air mixture stream 30th
  • FIGS. 3a and 3b in conjunction with the FIGS. 4a and 4b illustrate the operating principle of the fuel-air mixing device 12 according to the embodiment.
  • FIG. 3a shows a one-piece Venturi system according to the prior art.
  • fan 14 By arranged behind the fuel-air mixing device 12 fan 14 (see FIG. 1 ) is sucked through the air inlet 52 air 26.
  • the abscissa axis 56 in the FIGS. 4a and 4b forms the location along the longitudinal axis 55 and symmetry axis of the fuel-air mixing device 12 from.
  • the ordinate axis 58 shows a pressure 60 of the air 26 and / or a pressure 60 of the fuel-air mixture 30. Due to the narrowing cross-section or the decreasing cross-sectional area of the outer venturi 36, first the velocity of the air flow, the pressure 60, increases the air 26 sinks. At the first constriction 40, the pressure 60 of the air 26 reaches its minimum.
  • the nozzle 54 is disposed at the first throat 40 so that the fuel 28 is sucked by the air flow.
  • the pressure at the first constriction 40 is called control pressure 62.
  • the cross-sectional area of the outer venturi 36 widens in the flow direction or in the direction of the first outlet opening 44.
  • the pressure 60 of the fuel-air mixture 30 is increased.
  • the pressure 60 originally present at the inlet opening 52 is recovered.
  • pressure 60 differs from the pressure present at the inlet opening 52 by a pressure loss 64.
  • the lower the pressure loss 64 the lower the power consumption of the fan 14.
  • high modulation widths of the heater 10 are possible, that is, the ratio of the maximum possible heating power of the heater 10 to the minimum possible heating power of the heater 10 is high.
  • the pressure recovery between the first constriction 40 and the first outlet opening 44 is greater, the more the cross-sectional area of the outer venturi 36 increases from the first constriction 40 to the first outlet opening 44.
  • the pressure recovery between the first constriction 40 and the first outlet opening 44 is greater, the larger the cross-sectional area of the outer venturi 36 at the first outlet opening 44 compared to the cross-sectional area of the outer venturi 36 at the first constriction 40.
  • the greater the pressure recovery between the first constriction 40 and the first outlet opening 44 the lower the pressure loss 64.
  • venturi length 66 is the distance between the first constriction 40 and the first outlet opening 44.
  • the venturi length 66 must not fall below a minimum value, otherwise the flow breaks off and is no longer laminar. The minimum value of the venturi length 66 depends on the cross-sectional area of the outer venturi 36 at the first exit port 44 and the cross-sectional area of the outer venturi 36.
  • the cross sectional area of the outer venturi 36 at the first constriction is 1 cm 2
  • the cross sectional area of the outer venturi 36 at the first outlet 44 is 7 cm 2.
  • the venturi length 66 is 15 cm.
  • FIG. 3b is the fuel-air mixing device 12 of the embodiment and the course of the pressure 60 along the longitudinal axis 55 and symmetry axis of the fuel-air mixing device 12 shown.
  • at the same control pressure 62 and at the same pressure loss 64 with respect to the in FIG. 3a illustrated prior art requires a smaller venturi length 66. This allows the construction of a more compact fuel-air mixing device 12.
  • the outer venturi tube 36 receives a majority of the air 26a and the air flow (see FIG. 3b ).
  • the inner venturi 38 occupies a smaller portion of the air 26b and the Airflow on.
  • the fuel 28 is injected into the second constriction 42 of the inner venturi 38.
  • the second outlet opening 46 of the inner venturi 38 is arranged at the first constriction 40 of the outer Venturi tube 36.
  • At the first constriction 40 has the lowered by the outer Venturi tube pressure 60 a of the air flow and the fuel-air flow at its minimum.
  • the pressure 60b in the second constriction 42 is further lowered (see FIG. 3b ).
  • a control pressure 62 is reached, which is largely the control pressure 62 in in FIG. 3a shown system corresponds.
  • the control pressure 62 is generated at the second constriction 42, wherein only a portion of the total of the fuel-air mixing device 12 supplied air 26 must be accelerated to a maximum speed in the second constriction 42. Opposite the in FIG. 3a As shown in the one-piece Venturi system, the outer air 26a flows through a larger cross-sectional area at a lower speed. The pressure 60 can be recovered on a shorter venturi length 66.
  • FIG. 3b is the cross-sectional area of the outer Venturi tube 36 at the first outlet opening 44 7 cm ⁇ 2.
  • the cross-sectional area of the outer venturi 36 at the first constriction 40 is 2.7 cm 2.
  • the cross-sectional area of the inner Venturi tube 38 at the second outlet opening 46 is 0.5 cm ⁇ 2.
  • the cross-sectional area of the inner venturi 38 at the second constriction 42 is 0.3 cm ⁇ 2.
  • the venturi length 66 is 10 cm.
  • the cross-sectional area of the outer venturi 36 at the first throat 40 is between 30% and 60%, more preferably between 40% and 50% of the cross-section of the outer venturi 36 at the first exit port 44.
  • the cross sectional area of the inner venturi 38 at the second exit port 46 is between 5% and 30%, more preferably between 10% and 20% of the cross section of the outer venturi 36 at the first exit port 44.
  • the cross sectional area of the inner venturi 38 at the second throat 42 is between 40% and 70%, more preferably between 50% and 60%, of the cross section of the inner venturi 38 at the second exit orifice 46.
  • the second outlet opening 46 is arranged in the axial area at the first constriction 40.
  • the second outlet opening 46 is arranged on the longitudinal axis 55 or on an axis of symmetry of the outer venturi tube 36.
  • the control pressure 62 becomes minimal.
  • the pressure recovery is so maximum.
  • the second outlet opening 46 has a distance with respect to the constriction 40 with respect to the longitudinal direction 57. In this way, the control pressure 62 can be increased or adjusted over this distance. This may be advantageous, for example, for adapting the fuel-air mixing device 12 to different types of fuel.
  • the inner venturi 38 is axially displaceable relative to the outer Venturi tube 36. Depending on the position of the inner venturi 38, the distance of the second outlet opening 46 from the first constriction 40 changes. In this way, the control pressure 62 can be adjusted to a desired value, if necessary, during operation of the heating system 10. It is conceivable that the position of the inner Venturi tube 38 is adjustable by an electronic actuator, in particular by the control unit 22nd
  • the position of the nozzle 54 relative to the inner venturi 38 is axially adjustable. This way you can Distance of the nozzle 54 from the second constriction 42 with respect to the longitudinal direction 57 can be adjusted. In this way, the control pressure 62 can be adjusted to a desired value, if necessary, even during operation of the heating system 10. It is conceivable that the position of the nozzle 54 is adjustable by an electronic actuator, in particular by the control unit 22nd
  • the nozzle 54 and the inner Venturi tube 38 are axially adjustable. In this way, the control pressure 62 can be set particularly precisely and reliably.
  • the nozzle 54 is arranged concentrically within the inner venturi tube 38. In this way, the fuel 28 flows largely centrally into the guided through the inner venturi 38 air 26 b (see FIG. 3b ). In alternative embodiments, the nozzle 54 is not concentrically disposed in the outer venturi 36. Turbulence or turbulence in the fuel-air mixture 30 is promoted by the fuel 28 flowing asymmetrically into the air 26b. This can be advantageous for a particularly good mixing of the fuel-air mixture 30.
  • an axis of symmetry of the nozzle 54 has a distance between 10% and 50%, preferably between 20% and 40%, particularly preferably substantially 30% of a Venturi diameter of the inner Venturi tube 38 to the longitudinal axis 55 and / or to an axis of symmetry of the inner Venturi tube 38th It is conceivable that between the axis of symmetry of the nozzle 54 and the axis of symmetry of the inner venturi tube 38 there is an angle between 5 ° and 20 °, preferably between 10 ° and 15 °, in particular an adjustable angle. In this way, turbulence or turbulence in the fuel-air mixture 30 are favored.
  • the inner venturi 38 is disposed concentrically within the outer venturi 36. In this way, the fuel-air mixture 30 emerging from the inner venturi 38 flows largely centrally into the air 26a guided through the outer venturi tube 36 (see FIG FIG. 3b ). In alternative embodiments, the inner venturi 38 is not concentrically disposed in the outer venturi 36. As a result of the fuel-air mixture 30 flowing asymmetrically into the air 26a guided through the outer venturi tube 36, turbulences or swirling in the fuel-air mixture 30 flowing out of the first outlet opening 44 are promoted. This can be advantageous for a particularly good mixing of the fuel-air mixture 30.
  • an axis of symmetry of the inner venturi tube has a distance between 10% and 50%, preferably between 20% and 40%, particularly preferably substantially 30% of a Venturi diameter of the outer Venturi tube 36 to the longitudinal axis 55 and / or to the axis of symmetry of the outer Venturi tube 36th It is conceivable that an angle between 5 ° and 20 °, preferably between 10 ° and 15 °, is present between the axis of symmetry of the inner venturi tube 38 and the axis of symmetry of the outer venturi tube 36, in particular an adjustable angle. In this way, turbulence or turbulence in the fuel-air mixture 30 are favored.
  • the nozzle 54 and / or the inner venturi tube 38 is or are adjustable radially or perpendicular to the longitudinal axis 55 or symmetry axis of the fuel-air mixing device 12, in particular by an actuator. In this way, the strength of the turbulence or turbulence of the fuel-air mixture 30 is adjustable.
  • the outer venturi 36 has a circular cross-section.
  • the inner venturi 38 has a circular Cross-section.
  • the nozzle 54 has a circular cross section.
  • a fuel stream with a largely circular cross section is injected centrally into an air stream with a largely circular cross section. This allows a particularly laminar flow.
  • fuel-air mixing device 12 with alternative geometries of the cross sections of the outer venturi 36 and / or the inner venturi tube 38 and / or the nozzle 54 are conceivable.
  • the outer venturi tube 36, the inner venturi tube 38 and the nozzle 54 have a substantially rectangular and / or oval cross-section. In this way, the fuel 28 that has flowed into the air 26 has a different length and width in cross-section, which promotes the formation of flow instabilities and thus turbulence or turbulence.
  • the cross-section of the outer venturi 36 and / or the inner venturi 38 may vary along the length of the fuel-air mixer 12.
  • the outer venturi 36 may have a substantially circular cross-section, which changes only in the vicinity of the first outlet opening 44 continuously in an oval cross-section. In this way, turbulences or turbulences are promoted only as soon as a large part of the pressure 60 has been recovered.
  • the second inlet opening 50 is arranged at the first inlet opening 48 (see FIG. 2 ). In this way, turbulence or turbulence can be prevented, since so the directly past the inner Venturi tube 38 passing air 26a (see FIG. 3b ) has a low speed.
  • Alternative embodiments are conceivable in which the inner venturi tube 38 is arranged deeper in the outer venturi tube 36, so that the second inlet opening 50 has a larger distance with respect to the longitudinal direction 57 to the first inlet opening 48. In such embodiments, turbulence is or turbulence by an aerodynamically favorable form of the inner venturi tube 38 prevented.
  • the nozzle 54 has a fixed shape, in particular a constant opening cross-section.
  • the nozzle 54 has an adjustable throttle 68.
  • the throttle 68 is provided to reduce or adjust the pressure of the fuel 28 provided by the nozzle 54.
  • FIGS. 5a to 5c show a particular variant in which the throttle 68 is a replaceable fixed throttle 70.
  • the fixed throttle 70 forms the tail of the nozzle 54.
  • the fixed throttle 70 is provided in three different versions with a different pressure drop.
  • the fixed throttle 70 has a throttle plate 72.
  • the throttle plate 72 is mounted perpendicular to the flow direction of the fuel 28 in the fixed throttle. The fuel can flow only through a circular opening in the center of the throttle plate 72. In this way, the flow cross section of the fixed throttle 70 is reduced.
  • the fixed throttle 70 has different designs on different sized circular openings.
  • FIG. 5a shown embodiment of the fixed throttle 70 is provided for the use of L gas as a fuel 28.
  • FIG. 5b shown embodiment of the fixed throttle 70 is provided for the use of H gas.
  • FIG. 5c shown embodiment of the fixed throttle 70 is provided for the use of LPG.
  • LPG or Liquefied petroleum gas is also called LPG.
  • FIGS. 6a to 6c show a further variant of an adjustable throttle 68.
  • the nozzle 54 has a tapered tip, which has a third outlet opening 74 at its end.
  • the third exit opening 74 is provided to discharge the fuel 28 from the nozzle 54.
  • the throttle 68 is realized by a needle 76 arranged axially in the nozzle 54.
  • the needle 76 is within the nozzle 54 axially displaceable. In this way, the flow cross section of the nozzle 54 is reduced.
  • the needle 76 has a cross-section or a cross-sectional area, which largely corresponds to the cross-section or the cross-sectional area of the third outlet opening 74.
  • FIGS. 6a to 6c show different settings of the throttle 68 with the needle 76.
  • the in FIG. 6a shown adjustment of the throttle 68 is provided for the use of L gas.
  • the FIG. 6b shown adjustment of the throttle 68 is provided for the use of H gas.
  • the FIG. 6c shown adjustment of the throttle 68 is provided for the use of LPG.
  • the needle 76 is automatically adjustable, for example by an actuator.
  • the needle 76 can be adjusted by the controller 22. In this way, the throttle 68 can be adjusted during operation. This is advantageous for the rapid consideration of quality variations of the fuel 28.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
EP18197115.1A 2017-09-27 2018-09-27 Dispositif de mélange d'air/gaz de combustion et appareil de chauffage Active EP3462088B1 (fr)

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Application Number Priority Date Filing Date Title
DE102017217248.7A DE102017217248A1 (de) 2017-09-27 2017-09-27 Brennstoff-Luft-Mischeinrichtung und ein Heizgerät

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EP3462088A1 true EP3462088A1 (fr) 2019-04-03
EP3462088B1 EP3462088B1 (fr) 2021-04-07

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3822539A1 (fr) * 2019-11-12 2021-05-19 Robert Bosch GmbH Dispositif de mélange pour un appareil de chauffage par soufflerie

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Publication number Priority date Publication date Assignee Title
FR1315223A (fr) * 1961-12-08 1963-01-18 A D G Soc D Applic Des Gaz Perfectionnements aux appareils de chauffage à gaz
EP0149574B1 (fr) * 1984-01-13 1987-11-04 Compagnie De Raffinage Et De Distribution Total France Procédé de dilution dans de l'air d'un gaz ou d'un mélange gazeux, avant son rejet à l'atmosphère
DE10014347A1 (de) * 2000-03-24 2001-10-04 Webasto Thermosysteme Gmbh Zweistoff-Brenner mit Venturirohr-Brennstoffzerstäubung
DE102016201624A1 (de) 2016-02-03 2017-08-03 Robert Bosch Gmbh Brennstoff-Luft-Mischeinrichtung für ein Heizgerät

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DE582075C (de) * 1931-03-06 1933-08-08 Warren Doble Zerstaeuberbrenner fuer fluessige oder pulverfoermige Brennstoffe
US4004875A (en) * 1975-01-23 1977-01-25 John Zink Company Low nox burner
JPS55107816A (en) * 1979-02-13 1980-08-19 Hitachi Ltd Kerosene-gasifying burning device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1315223A (fr) * 1961-12-08 1963-01-18 A D G Soc D Applic Des Gaz Perfectionnements aux appareils de chauffage à gaz
EP0149574B1 (fr) * 1984-01-13 1987-11-04 Compagnie De Raffinage Et De Distribution Total France Procédé de dilution dans de l'air d'un gaz ou d'un mélange gazeux, avant son rejet à l'atmosphère
DE10014347A1 (de) * 2000-03-24 2001-10-04 Webasto Thermosysteme Gmbh Zweistoff-Brenner mit Venturirohr-Brennstoffzerstäubung
DE102016201624A1 (de) 2016-02-03 2017-08-03 Robert Bosch Gmbh Brennstoff-Luft-Mischeinrichtung für ein Heizgerät

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3822539A1 (fr) * 2019-11-12 2021-05-19 Robert Bosch GmbH Dispositif de mélange pour un appareil de chauffage par soufflerie

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DE102017217248A1 (de) 2019-03-28

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