EP0040393B1 - Dispositif de commande de la quantité d'air de combustion dans des installations de consommation à gaz avec brûleur d'injection - Google Patents

Dispositif de commande de la quantité d'air de combustion dans des installations de consommation à gaz avec brûleur d'injection Download PDF

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Publication number
EP0040393B1
EP0040393B1 EP81103668A EP81103668A EP0040393B1 EP 0040393 B1 EP0040393 B1 EP 0040393B1 EP 81103668 A EP81103668 A EP 81103668A EP 81103668 A EP81103668 A EP 81103668A EP 0040393 B1 EP0040393 B1 EP 0040393B1
Authority
EP
European Patent Office
Prior art keywords
gas
flow
air
obturators
injector
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
EP81103668A
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German (de)
English (en)
Other versions
EP0040393A1 (fr
Inventor
Hans Dipl.-Ing. Sommers
Kurt Cremer
Herbert Panek
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.)
EON Ruhrgas AG
Original Assignee
Ruhrgas AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ruhrgas AG filed Critical Ruhrgas AG
Priority to AT81103668T priority Critical patent/ATE8932T1/de
Publication of EP0040393A1 publication Critical patent/EP0040393A1/fr
Application granted granted Critical
Publication of EP0040393B1 publication Critical patent/EP0040393B1/fr
Expired legal-status Critical Current

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Classifications

    • 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 device for controlling the amount of combustion air in gas appliances with injector burners.
  • the combustion air throughput in gas appliances with injector burners results from the interaction of the gas impulse with the thermal uplift forces generated by the combustion and the flow resistances on the paths for the air, the fuel gas / combustion air mixture in front of and in the burner, and the exhaust gas up to flow control.
  • the object of the invention is to provide a device with which the amount of combustion air in gas appliances with injector burners can be controlled in such a simple manner that the air ratio or the fuel gas / combustion air ratio depends on the various operating conditions (partial load, full load, start-up state and when using different fuel gases) is as independent as possible, in particular in that the air ratio is kept constant regardless of the thermal load on the gas consumption device while maintaining the gas quality.
  • Influences that promote air flow are: forces from the gas pulse, from positive buoyancy and from (turbulent) deceleration resistances.
  • Influences that inhibit air flow are: forces from negative lift, from turbulent flow resistances (acceleration, deflection, deformation and friction resistances) and from laminar flow resistances. The sum of all forces acting on the flow is zero.
  • the coordination of the influences on one another is achieved according to the invention by means of a specifically set ratio between the gas pulse or the resulting force F G and the gas volume flow and / or by changing the flow characteristics of the combustion air or the gas-combustion air mixture in the gas consumption device, so that the laminar resistance component Installation of additional flow resistances or exchange of flow resistances with turbulent flow characteristics with those with laminar is increased.
  • the measures can be applied individually or combined with one another as desired.
  • the gas pulse flow tc of the gas flow q ⁇ emerging from the gas nozzle at the speed V ( j is known to be defined as
  • the nozzle cross section A is also constant and the following applies: ie the force changes with the square of the gas flow, ie the thermal load.
  • the new double nozzle for controlling the amount of combustion air consists of a housing with an inlet opening, an outlet opening, a throughflow opening inside the housing and a flow separation edge between the throughflow opening and outlet opening as well as two firmly connected spindles that can be moved in the axial direction, one of which is concentric in the outlet and the throughflow opening is arranged such that when the mandrels are moved together in the axial direction, the free passage cross sections of the openings increase or decrease as a function of the thermal load.
  • either the mandrel in the outlet opening or the mandrel in the throughflow opening can also serve as a shut-off device.
  • the shape of the mandrels depends on the desired change function of the force F G with the thermal load.
  • the spikes can e.g. B. be conical or spherical or have any curved surface lines. In this way, the new device differs in an advantageous manner from the known stopcock.
  • the gas connection is distributed over the two mandrels according to the free cross sections.
  • the housing is molded in the 'contrast to the cock plug of the known shut-off cock so as practical, but brings no pressure loss and no recovery of pressure from the kinetic energy after the first in the flow path of the gas mandrel.
  • Moving the mandrels can e.g. B. done by hand or by a signal from a heat load regulator.
  • the desired function between the force F G or the size of the air intake and the heat load is achieved by combining different mandrel shapes.
  • the desired change in the force F G with the thermal load is given below, then the type of necessary change in the free passage cross sections and then the structural embodiment of the mandrels with which the change can be achieved. If the heat load is reduced, the free passage cross section of the flow opening must be reduced and the free passage cross section of the outlet opening must be increased. The first mandrel (in the direction of flow of the gas) for changing the free passage cross section of the flow opening must be tapered and the second mandrel for changing the free passage cross section of the outlet opening must be flared. If the heat load is reduced, the free passage cross section of the throughflow opening must be in a different ratio be made smaller than that of the outlet opening. Both mandrels taper in the direction of flow of the gas.
  • the pitch angle of the mandrel for the outlet opening must differ from that of the mandrel for the throughflow opening. In some cases, it may be sufficient to taper only the mandrel for the outlet opening and to make the mandrel of the throughflow opening cylindrical. If the heat load is reduced, the free passage cross section of the throughflow opening must be larger and the free passage cross section of the outlet opening must be smaller. The first mandrel in the direction of flow of the gas is flared and the second tapered.
  • the double nozzle can be used alone or in conjunction with additional laminar flow resistances in gas appliances with moderately or weakly positive and neutral buoyancy influences, e.g. B. in gas water heaters, gas space heaters, gas special boilers, in hotplates and oven burners and in gas appliances with negative, that is, the flame direction opposite buoyancy, z. B. with downward-facing infrared radiators or grill burners.
  • moderately or weakly positive and neutral buoyancy influences e.g. B. in gas water heaters, gas space heaters, gas special boilers, in hotplates and oven burners and in gas appliances with negative, that is, the flame direction opposite buoyancy, z. B. with downward-facing infrared radiators or grill burners.
  • a laminar flow in the mixture path which is effective according to the invention can be forced by using a so-called laminar injector - instead of a turbulence injector - the diameter of which is chosen so that there is a laminar flow in it and that the acceleration resistance arising in the narrowest injector cross section is largely recovered in the diffuser.
  • the diffuser must therefore expand to at least twice, preferably four times, the narrowest cross section.
  • the opening angle is less than 8 °, preferably less than 4 '.
  • the invention can be applied regardless of whether the injectors supply the burner with the help of the gas pulse part of the air required for the combustion (primary air premixing) all the air required (stoichiometric air premixing) or even an excess of air (overstoichiometric air premixing).
  • the double nozzle 1 used in the outer wall space heater which is shown in FIG. 2, consists of a housing 7 with a gas inlet 8 and an outlet opening 12, the free passage cross section 14 of which can be changed by means of the displaceable conical mandrel 9.
  • the housing 7 there is a further displaceable mandrel 10 which can increase or decrease the free passage cross section 15 of the throughflow opening 13 and thus the nozzle pressure at the outlet opening 12.
  • the mandrel 9 widens conically in the direction of flow of the gas, the mandrel 10 tapers conically.
  • the mandrel 9 is rounded at the front to improve the flow.
  • the two mandrels are firmly connected to one another by means of adjusting spindle 11.
  • the tear-off edge 19 causes the flow to tear behind the flow opening 13.
  • the air throughput is reduced compared to the air requirement when the heat load decreases, and the influence of buoyancy is thus partially compensated for.
  • the remaining influences which increase the air throughput, are compensated for and the ratio of fuel gas and combustion air or the air ratio remains almost constant in the entire heat load range of the device.
  • FIG. 3 shows a gas infrared radiator with a double nozzle 1, which is shown enlarged in FIG. 4.
  • the pulse of the gas emerging from the adjustable double nozzle 1 leads the entire combustion air from the environment through the turbulence injector 16 from above to the ceramic perforated plate burner 17.
  • the gas burns on the upper surface of the burner plate in the combustion chamber 18 and the exhaust gases give most of it Heat content on the lower surface of the perforated plate burner. from where the heat is radiated downwards.
  • the exhaust gas then flows into the environment.
  • the adjustable double nozzle 1 shown in FIG. 4 consists of the same elements as the double nozzle shown in FIG. 2. The only difference to this is the shape of the spikes.
  • Mandrel 9 and mandrel 10 are both tapered in the direction of flow of the gas, the pitch angles being different.
  • the momentum is moved according to the relationship by simultaneously moving the mandrels in the direction of flow of the gas changed. This is achieved in that the free passage cross section 14 of the outlet opening 12 decreases more slowly than the free passage cross section 15 of the throughflow opening 13 when the thermal load is reduced (displacement of the mandrels in the direction of flow).
  • the heater works hygienically with the help of the double nozzle in a load range from 100% to 25% of the nominal heat load with a constant air ratio of 1.08.
  • the air ratio When using conventional nozzles, on the other hand, due to the negative influence of lift at full load, the air ratio must be approx. 1.5 - which means a lower efficiency in order to be able to achieve at least 50% of the nominal load as the smallest heat load at which the combustion is still hygienically perfect.
  • laminar injectors according to the invention were installed instead of the injectors with turbulent flow. While the air ratio originally rose from 1.15 to 1.45 when the heat load was reduced from 180% to approx. 40%, it remained constant after the device was retrofitted with laminar injectors.
  • the upstream of a laminar flow resistance e.g. B. a pack of narrow tubes in the airway in front of the turbulence injectors, has about the same effect.
  • the burning behavior when the heat load changes can be improved in all gas consumption devices with injector burners, because the ratio of fuel gas and combustion air or the air ratio remains constant over the entire control range of the burner.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)

Claims (7)

1. Dispositif de commande du débit d'air comburant dans les appareils d'utilisation du gaz équipés de brûleurs à induction, caractérisé par la présence de résistances d'écoulement constantes engendrant un écoulement laminaire dans le circuit d'air ou dans le circuit du mélange.
2. Dispositif de commande du débit d'air comburant dans les appareils d'utilisation du gaz équipé de brûleurs à induction, notamment selon la revendication 1, caractérisé par la présence d'un injecteur double dans le circuit gaz, qui comprend un boîtier (7) doté d'un orifice d'entrée (8), d'un orifice de sortie (12) et d'un orifice de passage (13) situé à l'intérieur du boîtier ainsi que deux obturateurs à mouvement axial solidaires l'un de l'autre (9, 10) et caractérisé par le fait que les deux obturateurs possèdent un dispositif de réglage (11), sont disposés dans l'axe de l'orifice de sortie (12) et de l'orifice de passage (13) de manière à faire varier les deux sections libres (14, 15) des ouvertures (12, 13) lorsqu'ils se déplacent en fonction du débit calorifique, et qu'il existe, entre l'orifice de passage (13) et l'orifice de sortie (12), une paroi (19) où se détache l'écoulement gazeux.
3. Dispositif selon la revendication 2, caractérisé par le fait que l'un des deux obturateurs (9, 10) solidaires d'une tige mobile commune s'élargit dans le sens d'écoulement du gaz et que l'autre se rétrécit dans le sens de l'écoulement.
4. Dispositif selon la revendication 2, caractérisé par le fait que les deux obturateurs (9, 10) solidaires d'une tige mobile commune se rétrécissent dans le sens de l'écoulement du gaz.
5. Dispositif selon l'une quelconque des revendications 2 à 4, caractérisé par le fait que les deux obturateurs (9, 10) solidaires d'une tige mobile commune ont une forme conique.
6. Dispositif selon l'une quelconque des revendications 1 à 5, caractérisé par le fait que la résistance d'écoulement placée dans le circuit d'air et engendrant un écoulement laminaire se compose d'un groupe de tubes jointifs.
7. Dispositif selon l'une quelconque des revendications 1 à 6, caractérisé par le fait que la résistance d'écoulement située dans le circuit du mélange et engendrant un écoulement laminaire se compose d'un (ou plusieurs) diffuseur(s) (2) (disposés les uns à côté des autres) dont la partie divergente présente un angle d'ouverture inférieur à 8° et de préférence inférieur à 4° et qui s'élargit pour atteindre au moins le double et de préférence au moins le quadruple de la section du col.
EP81103668A 1980-05-16 1981-05-13 Dispositif de commande de la quantité d'air de combustion dans des installations de consommation à gaz avec brûleur d'injection Expired EP0040393B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81103668T ATE8932T1 (de) 1980-05-16 1981-05-13 Vorrichtung zum steuern der verbrennungsluftmenge bei gasverbrauchseinrichtungen mit injektorbrennern.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803018752 DE3018752A1 (de) 1980-05-16 1980-05-16 Vorrichtung zum steuern der verbrennungsluftmenge bei gasverbrauchseinrichtungen mit injektorbrennern
DE3018752 1980-05-16

Publications (2)

Publication Number Publication Date
EP0040393A1 EP0040393A1 (fr) 1981-11-25
EP0040393B1 true EP0040393B1 (fr) 1984-08-08

Family

ID=6102589

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81103668A Expired EP0040393B1 (fr) 1980-05-16 1981-05-13 Dispositif de commande de la quantité d'air de combustion dans des installations de consommation à gaz avec brûleur d'injection

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EP (1) EP0040393B1 (fr)
AT (1) ATE8932T1 (fr)
DE (1) DE3018752A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3113416A1 (de) * 1981-04-03 1982-10-21 Ruhrgas Ag, 4300 Essen Verfahren zum betrieb eines einem luftstrom ausgesetzten gasbrenners sowie brenner zur durchfuehrung des verfahrens
AT398471B (de) * 1991-03-12 1994-12-27 Vaillant Gmbh Vormischgasbrenner

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB605432A (fr) * 1900-01-01
DE576326C (de) * 1932-04-08 1933-05-10 Max Nuss Dipl Ing Absperrhahn
DE685895C (de) * 1936-06-30 1939-12-27 Flaschengas Geraete G M B H In einer geteilten Gaskammer angeordnetes federbelastetes, von aussen handbetaetigtes und als Doppelventil ausgebildetes Gasschaltventil
DE675326C (de) * 1937-11-27 1939-05-05 Fortuna Werke Spezialmaschinen Bandmesserspaltmaschine
US2547276A (en) * 1947-02-28 1951-04-03 Herbert H Marsh Gas burner with gas preheating chamber and flame nozzles
BE764407A (fr) * 1971-03-17 1971-08-16 Four Industriel Belge Dispositif pour le dosage d'un melange de deux gaz.
FR2373750A1 (fr) * 1976-12-09 1978-07-07 Louyot Comptoir Lyon Alemand Bec pour bruleur a flammes de premelange presentant une structure multicanaux constituee d'un metal avec un revetement ceramique ou vitreux

Also Published As

Publication number Publication date
ATE8932T1 (de) 1984-08-15
DE3018752A1 (de) 1981-11-26
EP0040393A1 (fr) 1981-11-25

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