EP1584868B1 - Zylindrischer Brenner - Google Patents

Zylindrischer Brenner Download PDF

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Publication number
EP1584868B1
EP1584868B1 EP20050252224 EP05252224A EP1584868B1 EP 1584868 B1 EP1584868 B1 EP 1584868B1 EP 20050252224 EP20050252224 EP 20050252224 EP 05252224 A EP05252224 A EP 05252224A EP 1584868 B1 EP1584868 B1 EP 1584868B1
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EP
European Patent Office
Prior art keywords
top end
heat chamber
inlet pipe
distribution
chamber
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 - Fee Related
Application number
EP20050252224
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English (en)
French (fr)
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EP1584868A3 (de
EP1584868A2 (de
Inventor
Misako Rinnai Corporation Tachi
Yoshihiko Rinnai Corporation Takasu
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Rinnai Corp
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Rinnai Corp
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Publication date
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Publication of EP1584868A2 publication Critical patent/EP1584868A2/de
Publication of EP1584868A3 publication Critical patent/EP1584868A3/de
Application granted granted Critical
Publication of EP1584868B1 publication Critical patent/EP1584868B1/de
Expired - Fee Related 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
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/101—Flame diffusing means characterised by surface shape
    • F23D2203/1012—Flame diffusing means characterised by surface shape tubular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/102—Flame diffusing means using perforated plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2212/00—Burner material specifications
    • F23D2212/10—Burner material specifications ceramic

Definitions

  • the present invention relates to a cylindrical burner that is used in a spiral water pipe heat exchanger and the like.
  • a spiral water pipe heat exchanger in which, as shown in FIG. 1 , a spiral condensed water pipe 101 and a spiral heating water pipe 102 are housed in a housing 100 and a cylindrical burner A serving as a heat source is arranged in a space surrounded by the heating water pipe 102.
  • An upstream end of the condensed water pipe 101 is connected to a water supply header 103, a downstream end of the condensed water pipe 101 and an upstream end of the heating water pipe 102 are connected with each other via a relay header 104, and a downstream end of the heating water pipe 102 is connected to an outlet hot water header 105.
  • a cylindrical burner including: a heat chamber, in a peripheral surface of which a plurality of burner ports are opened; a base plate having an inlet port mounted at a base end of the heat chamber; and a cover plate mounted at a top end of the heat chamber, wherein mixed gas flowing in an internal space of the heat chamber from the inlet port is jetted from the burner ports of the heat chamber and burnt (see, for example, Japanese Utility Model Publication No. Sho 61-26737 ).
  • the heat chamber is constituted by combining plural strip-like combustion plates of ceramics having a plurality of burner ports in a cylindrical shape.
  • a distribution pipe which partitions the space in the heat chamber into inner and outer two chambers, extending in an axial direction from the base plate to the cover plate in the inside of the heat chamber, causing the mixed gas to flow into the inner chamber on the inner side of the distribution pipe from the inlet port, and causing the mixed gas, which has flown into the inner chamber, to flow into the outer chamber on the outer side of the distribution pipe via a plurality of distribution holes formed in the distribution pipe. Consequently, pressure distribution in an axial direction in the outer chamber is uniformalized by reducing an arrangement density of the distribution holes on a top end side of the distribution pipe. Thus, it is possible to uniformalize the axial direction distribution of the jet quantity of the mixed gas from the heat chamber.
  • Such a cylindrical burner is known from US 5240411 .
  • the fuel pipe B is formed in an L shape bending in a direction perpendicular to the axial direction of the heat chamber (in a radial direction of the heat chamber) in order to reduce a space occupied by the fuel pipe B. Therefore, the mixed gas flows into the inlet port from the fuel pipe while keeping a motion component in the radial direction of the heat chamber. A jet quantity of the mixed gas from the heat chamber increases in a peripheral direction portion matching this radial direction. As a result, a peripheral direction distribution of the jet quantity of the mixed gas is made non-uniform.
  • embodiments of the invention seek to provide a cylindrical burner that can advantageously uniformalize distributions of a jet quantity of the mixed gas from a heat chamber in both a peripheral direction and an axial direction such that uniform combustion is preferably performed over an entire area on a peripheral surface of the heat chamber, even if mixed gas flows in from an inlet port which has or maintain a component of motion in a radial direction with respect to the heat chamber.
  • a cylindrical burner including: a heat chamber, in a peripheral surface of which a plurality of burner ports are opened; a base plate having an inlet port mounted at a base end of the heat chamber; a cover plate mounted at a top end of the heat chamber; and a distribution pipe, which partitions the space in the heat chamber into inner and outer two chambers, extending in an axial direction from the base plate to the cover plate in the inside of the heat chamber, the cylindrical burner causing the mixed gas to flow into an inner chamber on an inner side of the distribution pipe from the inlet port and causing the mixed gas, which has flown into the inner chamber, to flow into an outer chamber on an outer side of the distribution pipe via a plurality of distribution holes formed in the distribution pipe, wherein an inlet pipe is connected to the inlet port.
  • the inlet pipe extends in the axial direction to a position closer to a top end of the distribution pipe, is arranged in the inner chamber, an annular baffle board, which is located in a section a predetermined distance apart from a top end of the inlet pipe to a base end side of the distribution pipe and narrows a gap between an outer periphery of the distribution pipe and an inner peripheral surface of the heat chamber, is arranged in the outer periphery of the distribution pipe, and assuming that an opening area of distribution holes per a unit area of the distribution pipe is a distribution hole density, the distribution hole density falls to zero or a very small value near zero in a portion closer to the top end of the inlet pipe in an axial direction area between the top end of the inlet pipe and the top end of the distribution pipe and a portion between the top end of the inlet pipe and the portion near the arrangement section of the baffle board.
  • the mixed gas is rectified to a flow, which hardly has a motion component in the radial direction, in a process of passing the inlet pipe.
  • a peripheral direction distribution of the jet quantity of the mixed gas from the heat chamber is advantageously uniformalized.
  • a distribution hole density in the portion (the "c" area) closer to the top end of the inlet pipe in the axial direction area between the top end of the inlet pipe and the top end of the heat chamber is set to substantially zero.
  • the mixed gas flows into the outer chamber from distribution holes in a limited portion other than the portion closer to the top end of the inlet pipe (the "c" area).
  • the mixed gas which has flown into the outer chamber, flows in the outer chamber toward the base end side.
  • the mixed gas is prevented from flowing further to the base end side by the baffle board in the outer periphery of the distribution pipe. Note that, in a portion between the top end of the inlet pipe and the position near the arrangement section of the baffle board (an area indicated by "d" in FIG.
  • the velocity of flow of the mixed gas flowing to the outer peripheral void of the inlet pipe is high and the pressure in the outer peripheral void of the inlet pipe tends to be negative.
  • the mixed gas, which has flown into the outer chamber is sucked into the outer peripheral void of the inlet pipe.
  • distribution hole density in the portion between the top end of the inlet pipe and the position near the arrangement section of the baffle board (the "d" area) is preferably set to substantially zero, the mixed gas, which has flown into the outer chamber, is advantageously never sucked into the outer peripheral void of the inlet pipe.
  • the pressure distribution of the mixed gas in the portion of the outer chamber between the arrangement section of the baffle board and the top end of the heat chamber is easily uniformalized by setting the distribution hole density to substantially zero and by a function of the baffle board.
  • the axial direction distribution of the jet quantity of the mixed gas from the heat chamber between the arrangement section of the baffle board and the top end of the heat chamber may be uniformalized.
  • a leading end in the axial direction in the burner port opened area of the heat chamber is set to be located in the portion closer to the top end of the inlet pipe (the "c" area) in the axial direction area between the top end of the inlet pipe and the top end of the heat chamber or the portion between the top end of the inlet pipe and the portion near the arrangement section of the baffle board (the “d” area). Consequently, there is no burner ports in the axial direction position matching the portion where the distribution holes are formed in the axial direction area between the top end of the inlet pipe and the top end of the heat chamber. Thus, the deficiency described above never occurs.
  • the distribution hole density in the portion other than the portion closer to the top end of the inlet pipe (the "c" area) in the axial direction area between the top end of the inlet pipe and the top end of the distribution pipe is set appropriately such that the mixed gas pressure in the outer chamber in the area from the arrangement section of the baffle board to the top end of the heat chamber and the mixed gas pressure in the outer chamber in the area from the arrangement section of the baffle board to the base end of the heat chamber are equal. Consequently, it is possible to uniformalize the axial direction distribution of the jet quantity of the mixed gas from the heat chamber over the entire length of the heat chamber. Therefore, it is possible to obtain uniform combustion over the entire peripheral area of the heat chamber in conjunction with the uniformalization of the peripheral direction distribution of the jet quantity of the mixed gas from the heat chamber due to the action of the inlet pipe.
  • a cylindrical burner in an embodiment of the invention shown in FIG. 2 is a burner that is used as a heat source for a spiral water pipe heat exchanger in FIG. 1 .
  • This burner includes a heat chamber 1 of a cylindrical shape, a base plate 2 mounted at a base end of the heat chamber 1, and a cover plate 3 mounted at a top end of the heat chamber 1.
  • the heat chamber 1 is constituted by combining plural (six in an example shown in the figure) strip-like combustion plates 1b of ceramics, which have a plurality of burner ports 1a, in a cylindrical shape.
  • a distribution pipe 4 extending in an axial direction thereof from the base plate 2 to the cover plate 3 is provided in the heat chamber 1.
  • the distribution plate 4 is formed in a hexagonal cylindrical shape similar to an inner surface shape of the heat chamber 1.
  • Apluralityof distribution holes 4a are formed on a peripheral surface of the distribution pipe 4 in a predetermined layout described later.
  • the distribution pipe 4 is fixed to the base plate 2 at a base end thereof by spot welding or the like.
  • a cap 4b is fastened to a top end of the distribution pipe 4.
  • a projected portion 4c which is fit and inserted in an inner periphery of the cover plate 3 formed in an annular shape, is formed in this cap 4b.
  • the distribution pipe 4 is inserted into the heat chamber 1 to set the base plate 2 in abutment against an end face on the base end side of the heat chamber 1 via a packing 5.
  • the cover plate 3 is set in abutment against an end face on the top end side of the heat chamber 1 via another packing 5.
  • the projected portion 4c is inserted into the inner periphery of the cover plate 3.
  • the projected portion 4c is crushed inwardly in the axial direction. Consequently, the cover plate 3 is caulked and fixed to the distribution pipe 4 in a state in which the cover plate 3 is pressed inwardly in the axial direction.
  • the heat chamber 1 is held firmly between the base plate 2 and the cover plate 3.
  • annular seat plate 6 opposed to the end face on the base end side of the heat chamber 1 is fixed to the base plate 2 by spot welding or the like.
  • Annular flange sections 6a and 3a bending inwardly in the axial direction are formed in outer peripheries of the seat plate 6 and the cover plate 3, respectively, such that the packings 5 do not deviate in the radial direction.
  • An inner space of the heat chamber 1 is partitioned into an inner chamber 7 on an inner side of the distribution chamber 4 and an outer chamber 8 on an outer side of the distribution pipe 4 by the distribution pipe 4.
  • an inlet port 2a in which a mixture of fuel gas and primary air forcibly supplied from a fuel pipe B is caused to flow, is provided in the base plate 2.
  • the inlet pipe 9 is provided to rectify the mixed gas, which flows into the inlet port 2a from the fuel pipe B bending in the radial direction of the heat chamber 1 while keeping a motion component in the radial direction of the heat chamber 1, to a flow, which hardly has the motion component in the radial direction, and cause the mixed gas to flow into the inner chamber 7.
  • Peripheral direction distribution of the jet quantity of the mixed gas from the heat chamber 1 is uniformalized by this rectifying action.
  • a distance L2 between a top end of the inlet pipe 9 and the top end of the heat chamber 1 is set in a range of 15 to 35% of a total length L1 of the heat chamber 1. A reason for this is as described below.
  • the distance L2 is shorter than the distance in this range, mixed gas pressure between the top end of the inlet pipe 9 and the top end of the distribution pipe 4 is made excessive and an outflow resistance of the mixed gas from the inlet pipe 9 increases to increase a pressure loss of the burner.
  • the distance L2 is longer than the distance in the range, the mixed gas cannot be sufficiently rectified to the flow, which does not have the radial direction motion component, due to the insufficient length of the inlet pipe 9.
  • a portion on the inner peripheral side of the cover plate 3 is sunken inwardly in the axial direction in order to increase rigidity of the cover plate 3.
  • a length of the distribution pipe 4 is shorter than a length of the heat chamber 1 because of the sunken portion. Even in this case, the pressure loss of the burner does not increase so much if the distance L2 between the top end of the inlet pipe 9 and the top end of the heat chamber 1 is set to about 15% or more of the total length L1 of the heat chamber 1.
  • An annular baffle board 10 which narrows a gap between an outer periphery of the distribution pipe 4 and an inner peripheral surface of the heat chamber 1, is provided in the outer periphery of the distribution pipe 4 in a position a predetermined distance L3 apart to the base end side of the distribution pipe 4 from the top end of the inlet pipe 9. It is preferable that the baffle board 10 narrows the gap between the inner peripheral surface of the heat chamber 1 and the outer peripheral surface of the distribution pipe 4 (a radial direction width of the outer chamber 8) to be half or less.
  • the gap is set such that a ratio of H1 and H2 is about 4:3.
  • the distance L3 is set in a range of 80 to 100% of the distance L2 between the top end of the inlet pipe 9 and the top end of the heat chamber 1. A reason for this will be described later.
  • An arrangement pattern of the distribution holes 4a formed in the distribution pipe 4 is set as described below in relation to the inlet pipe 9 and the baffle board 10.
  • the heat chamber 1 is sectioned in the axial direction as follows. A portion closer to the top end of the heat chamber 1 in the axial direction area between the top end of the heat chamber 1 and the top end of the inlet pipe 9 is set as an "a" area, a middle portion in the axial direction area between the top end of the heat chamber 1 and the top end of the inlet pipe 9 is set as a "b" area, a portion closer to the top end of the inlet pipe 9 in the axial direction area between the top end of the heat chamber 1 and the top end of the inlet pipe 9 is set as a "c" area, a portion between the top end of the inlet pipe 9 and the portion near the arrangement section of the baffle board 10 is set as a "d” area, a portion near the arrangement portion of the baffle board 10 around the baffle board 10 is set as an "e” area, and
  • the distribution holes 4a are formed only in the "b” area, the "e” area, and the “f” area and are not formed in the "a” area, the "c” area, and the “d” area. Assuming that an opening area of the distribution holes 4a per a unit area of the distribution pipe 4 is the distribution hole density, distribution hole densities in the "b” area and the “e” area are set larger than the distribution hole density in the "f” area. Incidentally, distribution hole densities in the a, c, and "d” areas are zero.
  • axial direction widths of the a, b, and "c" areas are set to a width obtained by equally dividing the axial direction area between the top end of the heat chamber 1 and the top end of the inlet pipe 9 into three parts, that is, L2/3 and an axial direction with of the "e" area is also set to L2/3.
  • the remaining mixed gas flows to a void in the inner chamber 7 between the inlet pipe 9 and the distribution pipe 4 (hereinafter referred to as an outer peripheral void of the inlet pipe 9) and flows into the outer chamber 8 from the distribution holes 4a in the "e" area and the "f" area.
  • the mixed gas which should be caused to flow into the outer peripheral void of the inlet pipe 9, flows to the outer chamber 8 via the distribution holes in the "c" area.
  • the amount of the mixed gas flowing into the outer peripheral void of the inlet pipe 9 is made insufficient.
  • the distribution holes 4a are not formed in the "c" area, it is possible to supply the mixed gas sufficiently to the outer peripheral void of the inlet pipe 9. Therefore, it is possible to uniformalize the axial direction distribution of the mixed gas pressure in the outer chamber 8 in the area from the arrangement section of the baffle board 10 to the base end of the heat chamber 1 by appreciately setting the distribution hole density in "f" area. As a result, it is possible to uniformalize an axial direction distribution of the jet quantity of the mixed gas from the burner ports 1a of the heat chamber 1 in this area.
  • the predominant flow of the mixed gas in the outer peripheral void of the inlet pipe 9 changes to a flow in the axial direction.
  • the mixed gas flows into the outer chamber 8 from the distribution holes 4a less easily and mixed gas pressure in the portion of the outer chamber 8 closer to the arrangement section of the baffle board 10 tends to be low.
  • the distribution hole density in the "e" area near the arrangement section of the baffle board 10 is set large. Therefore, the mixed gas flows into the outer chamber 8 from the distribution holes 4a in the "e” area easily. As a result, drop in mixed gas pressure in the portion of the outer chamber 8 closer to the arrangement section of the baffle board 10 is compensated.
  • the mixed gas which has flown into the outer chamber 8 from the distribution holes 4a in the "b" area, flows toward the base end side of the heat chamber 1 in the outer chamber 8.
  • the velocity of flow of the mixed gas flowing to the outer peripheral void of the inlet pipe 9 is high and the pressure in the outer peripheral void of the inlet pipe 9 tends to be negative. Therefore, if the distribution holes 4a are formed in the "d” area, the mixed gas in the outer chamber 8 is sucked into the outer peripheral void of the inlet pipe 9.
  • the mixed gas which has flown into the outer chamber 8 from the distribution holes 4a in the "b" area, flows toward the base end side of the heat chamber 1 in the outer chamber 8 without being sucked into the outer peripheral void of the inlet pipe 9.
  • the mixed gas flows directly to the base end in the outer chamber 8
  • pressure in the "d" area of the outer chamber 8 falls.
  • the mixed gas is prevented from further flowing toward the base end side by the baffle board 10.
  • pressure distribution of the mixed gas in a portion of the outer chamber 8 between the arrangement section of the baffle board 10 and the top end of the heat chamber 1 is uniformalized easily.
  • the burner ports 1a are present in the "b" area, the mixed gas, which has flown in from the distribution holes 4a in the "b” area, proceeds straight to the outside in the radial direction toward the burner ports in the "b” area directly. As a result, the jet quantity of the mixed gas from the burner ports in the "b” area is made excessive.
  • the burner ports 1a are not formed in order to prevent flames from touching the flange sections 3a and 6a to generate CO or prevent the flange sections 3a and 6a from deteriorating.
  • a leading end of a burner port forming area of the heat chamber 1 is located in the "c" area.
  • the "b" area is a non-burner port portion where no burner port 1a is present.
  • the mixed gas which has flown in from the distribution holes 4a in the "b" area, is prevented from proceeding to the outside in the radial direction directly and jetting from the burner ports 1a. Therefore, the axial direction distribution of the jet quantity of the mixed gas from the burner ports 1a of the heat chamber 1 between the arrangement section of the baffle board 10 and the top end of the heat chamber 1 is uniformalized in conjunction with pressure equalization by the function of the baffle board 10. Note that the leading end of the burner port forming area of the heat chamber 1 may be located in the "d" area.
  • dummy burner ports 1c of a blank hole shape are formed in non-burner port portion at the respective ends of the heat chamber 1 because of a reason relating to formation such as uniformalization of a shrinking percentage at the time of firing of the ceramics combustion plate 1b.
  • the portion of the outer chamber 8 between the arrangement section of the baffle board 10 and the top end of the heat chamber 1 and the portion of the outer chamber 8 between the arrangement section of the baffle board 10 and the base end of the heat chamber 1 are not blocked completely but communicate with each other via a gap between the baffle board 10 and the inner peripheral surface of the heat chamber 1.
  • a large pressure difference is not caused on both sides of the baffle board 10.
  • the distribution hole density in the "b" area is set appropriately such that mixed gas pressure in the outer chamber 8 in the area from the arrangement section of the baffle board 10 to the top end of the heat chamber 1 and a mixed gas pressure in the outer chamber 8 in the area from the arrangement section of the baffle board 10 to the base end of the heat chamber 1 are substantially equal, it is possible to uniformalize the axial direction distribution of the jet quantity of the mixed gas from the burner ports 1a of the heat chamber 1 over the entire length of the heat chamber 1. It is possible to obtain uniform combustion over an entire area of the burner port forming area of the heat chamber 1 in conjunction with uniformalization of the peripheral direction distribution of the jet quantity of the mixed gas from the burner ports 1a of the heat chamber 1 due to a rectifying action of the inlet pipe 9.
  • the distribution holes 4a from the "b" area to the "a" area.
  • a portion of the "a" area in the inner chamber 7 is a portion where the mixed gas flowing out in the axial direction from the inlet pipe 9 comes to a dead end.
  • pressure of the mixed gas is extremely high in the portion. Therefore, if the distribution holes 4a are formed in the "a” area, a large amount of the mixed gas flows to the outer chamber 8 in the "a” area and cannot be supplied to the outer peripheral void of the inlet pipe 9 sufficiently. In this embodiment, since the distribution holes 4a are not formed in the "a” area, such deficiency never occurs.
  • the distance L3 between the top end of the inlet pipe 9 and the baffle board 10 is set in the range of 80 to 100% of the distance L2 between the top end of the inlet pipe 9 and the top end of the heat chamber 1 as described above. A reason for this is as described below.
  • the distance L3 is shorter than the distance in the range, a portion, where a pressure of the outer peripheral void of the inlet pipe 9 tends to be negative, enters an area between the arrangement section of the baffle board 10 and the base end of the heat chamber 1.
  • mixed gas pressure in the portion of the outer chamber 8 closer to the arrangement section of the baffle board 10 in this area falls.
  • no distribution holes 4a are formed in the a, c, and "d" areas.
  • a few distribution holes 4a may be formed in the a, c, and "d" areas as long as distribution hole density is a very small value near zero.
  • the cylindrical burner in the embodiment is suitable as a burner for a heat source of a spiral water pipe heat exchanger, an application of the invention is not limited to this.

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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)

Claims (5)

  1. Zylindrischer Brenner, umfassend:
    eine Heizkammer (1), in deren Randfläche eine Anzahl Brenneröffnungen (1a) geöffnet ist;
    eine Basisplatte (2), die an einem Basisende von Heizkammer (1) befestigt ist;
    eine Abdeckplatte (3), die am oberen Ende von Heizkammer (1) befestigt ist;
    ein Verteilerrohr (4), das in axialer Richtung von der Basisplatte (2) zur Abdeckplatte (3) im Inneren der Heizkammer (1) verläuft, wobei das Verteilerrohr (4) den Raum in der Heizkammer in eine Innenkammer (7) auf einer Innenseite des Verteilerrohrs (4) und eine Außenkammer (8) auf einer Außenseite des Verteilerrohrs (4) unterteilt;
    wobei die Basisplatte (2) eine Einlassöffnung (2a) aufweist, die es ermöglicht, dass Mischgas in die Innenkammer (7) strömt, und das Verteilerrohr (4) eine Anzahl Verteilerlöcher (4a) umfasst, die in dem Verteilerrohr (4) herausgearbeitet sind, und die es ermöglichen, dass das Mischgas von der Innenkammer zur Außenkammer (8) strömt;
    ein Einlassrohr (9), das in der Innenkammer (7) angeordnet ist, wobei das Einlaßrohr (9) an die Einlassöffnung (2a) angeschlossen ist,
    dadurch gekennzeichnet, dass
    das Einlassrohr (9) in axialer Richtung zum oberen Ende der Heizkammer verläuft;
    eine ringförmige Umlenkplatte (10) in einem Außenrand von Verteilerrohr (4) angeordnet ist, und sie sich in einem Abschnitt in einer festgelegten Distanz (L3) vom oberen Ende des Einlassrohrs (9) entfernt zu einem Basisende des Verteilerrohrs (4) befindet, wobei die Umlenkplatte (10) einen Spalt zwischen dem Außenrand von Verteilerrohr (4) und einer Innenrandfläche der Heizkammer (1) verengt;
    und dass die Verteilerlochdichte in einem Bereich zwischen dem oberen Ende von Einlassrohr (9) und dem oberen Ende der Heizkammer in einem Teil (c) zum oberen Ende von Einlassrohr (9) auf etwa Null fällt und wobei die Verteilerlochdichte in einem Teil (d) zwischen dem oberen Ende von Einlassrohr (9) und einem Teil (e) nahe dem Anordnungsbereich der Umlenkplatte (10) auf etwa Null fällt.
  2. Zylindrischer Brenner nach Anspruch 1, wobei sich ein vorderes Ende in axialer Richtung eines Brenneröffnungsbereichs der Heizkammer (1) in Teil (c) zum oberen Ende des Einlassrohrs (9) oder Teil (d) zwischen dem oberen Ende von Einlassrohr (9) und Teil (e) nahe dem Anordnungsabschnitt der Umlenkplatte (10) befindet.
  3. Zylindrischer Brenner nach Anspruch 1 oder 2, wobei die Verteilerlochdichte in Teil (e) nahe dem Anordnungsbereich von Umlenkplatte (10) größer ist als die Verteilerlochdichte in Teil (f) zwischen dem Basisende der Heizkammer (1) und dem Teil (e) nahe dem Anordnungsbereich von Umlenkplatte (10).
  4. Zylindrischer Brenner nach Anspruch 1, 2 oder 3, wobei der Bereich zwischen dem oberen Ende von Einlassrohr (9) und dem oberen Ende von Heizkammer (1) in drei Teile unterteilt ist, nämlich den Teil (c) zum oberen Ende von Einlassrohr (9), einen Mittelteil (b) und einen Teil (a) zum oberen Ende von Heizkammer (1), und wobei die Verteilerlochdichte in Teil (a) zum oberen Ende von Heizkammer (1) etwa Null ist, und die Verteilerlöcher konzentriert im Mittelteil (b) herausgearbeitet sind.
  5. Zylindrischer Brenner nach einem der Ansprüche 1 bis 4, wobei eine Distanz (L2) zwischen dem oberen Ende von Einlassrohr (9) und dem oberen Ende von Heizkammer (1) in einem Bereich von 15 bis 35% der Gesamtlänge von Heizkammer (1) eingestellt wird, und eine Distanz (L3) zwischen dem oberen Ende von Einlassrohr (9) und der Umlenkplatte (10) in einem Bereich von 80 bis 100% der Distanz zwischen dem oberen Ende von Einlassrohr (9) und dem oberen Ende von Heizkammer (10) eingestellt wird.
EP20050252224 2004-04-09 2005-04-08 Zylindrischer Brenner Expired - Fee Related EP1584868B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004115349 2004-04-09
JP2004115349A JP3958754B2 (ja) 2004-04-09 2004-04-09 筒状バーナ

Publications (3)

Publication Number Publication Date
EP1584868A2 EP1584868A2 (de) 2005-10-12
EP1584868A3 EP1584868A3 (de) 2006-03-15
EP1584868B1 true EP1584868B1 (de) 2015-01-14

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ITMI20061961A1 (it) * 2006-10-13 2008-04-14 Polidoro S P A Distributore differenziato specie per bruciatori premiscelati
US8050403B2 (en) 2007-03-06 2011-11-01 Research In Motion Limited Method and apparatus for generating a public key in a manner that counters power analysis attacks
ITMO20070167A1 (it) * 2007-05-21 2008-11-22 Worgas Bruciatori Srl Bruciatore modulante
CN102597624B (zh) * 2009-12-11 2015-04-15 贝卡尔特燃烧技术股份有限公司 具有低孔隙率的燃烧器层面的燃烧器
WO2021057677A1 (zh) * 2019-09-23 2021-04-01 苏州威博特能源环保科技有限公司 一种冷凝锅炉

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EP1584868A3 (de) 2006-03-15
JP3958754B2 (ja) 2007-08-15
JP2005299998A (ja) 2005-10-27
EP1584868A2 (de) 2005-10-12

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