FR2677110A1 - BURNER WITH AT LEAST ONE MULTIPLE SPOUT TUBE AND COOLING BODIES. - Google Patents

Abstract

Burner with at least one tube with multiple nozzles, supplied with a combustible mixture and provided with radial nozzles arranged essentially along a generatrix of the tube, cooling bodies being provided at a certain distance from and above said tube, and more or less less parallel to it. To quickly stabilize the flames of such a burner while it is in operation, provision is made to design the cooling bodies (4) in the form of plates and to place them on either side of the rows of the nozzles, thus limiting laterally the zone occupied by flames (3).

Description

The present invention relates to a burner with

  less a multi-nozzle tube fed with a mixture of

  bustible and equipped with radial nozzles arranged essentially

  along a generatrix of the tube, cooled bodies

  being provided at a certain distance and above

  said tube, and more or less parallel to it.

  On such burners, there is, during combustion

  mixture of combustible gas and air,

  nized by the multi-needle tube and issuing out of

  be by a series of orifices, addition of secondary air coming from the combustion chamber o the tube or tubes to

multiple beaks are arranged.

  The cooling bodies ensure an evacuation of

  the heat of the flames environment, which is

  duit by a cooling of these flames and thereby by

  a significant reduction on the part of N Ox.

  On known burners, these bodies have a section

  essentially circular, which has the consequence -

  as experience shows that the stabilization of these flames takes a long time and that combustion can

  easily be troubled by insignificant causes.

  The present invention aims to avoid these inconveniences

  in proposing a burner of the type mentioned above, guaranteeing a great stability of the combustion and of which

  operation largely avoids the issuance of

  cifs. According to the invention, it is therefore proposed to design the cooling bodies in the form of plates and to arrange them on either side of the rows of the nozzles,

  thereby limiting the area occupied by the flames

my.

  As a result of this arrangement of the plates, it obtains

  -2- holds a very fast stabilization of the flames so that the operation of the burner finishes in a very short time, after its start, to stabilize, which also contributes to reducing the emission of pollutants which appear in particular during the transition period before stabilization. The section of the plates can, to a large extent, be arbitrary, either rectangular, S-shaped, or having a projecting curvature. In addition, plates having a cross section with a fold or

who have a wing profile.

  According to another characteristic of the invention,

  a ratio of 0.5 to 13.4 can be expected between the distance

  this lower edges of the plates and the generator the

  higher of the multi-needle tube on the one hand and the

  flames at the point of contact with the beak of the tu-

be, on the other.

  Another advantageous dimensioning results from a

  0.25 to 16 port between the length of the front face

  plates and the distance from the lower edges of the

  vis-à-vis the highest generator of the tube to

multiple beaks.

  It is also advantageous to arrange the plates

  from a certain angle vis-à-vis the vertical, the report

  between the free distance of the plates of a tube with multiple nozzles in their lower part and that in their

  upper part being from 1.036 to 10.238.

  In addition, it may be provided that the free distance between

  be the plates of a tube with multiple beaks in their

  lower section corresponds to the width of the flames in

  contact with the nozzle, plus a supplement of 4 to 20 mm.

  By doing so, we obtain conditions of

  particularly favorable for secondary air

  around the flames, which contributes to a rapid

fire spreading.

  According to another characteristic of the invention, it can be provided that the cooling bodies arranged on different sides of two neighboring multi-nozzle tubes,

  are connected to each other by a plain board.

  This provides the advantage that secondary air in its

  can only flow upwards between

  cooling and flames, which

  consequently to direct the flames and to reduce the formation of N Ox, in particular the rapid formation of N Ox as a result

  the higher oxygen content in the zone of com-

  In addition, there is also penetration of

  secondary air in the flames and thereby their

  a significant amount of oxygen, which is

  resulting in almost complete combustion of the

  tible, thus largely avoiding the emission of CO. This results in a largely

  pollutants and a slight improvement in the

the burner.

  The consequence is an increase in the air coefficient in the area concerned, reaching values that

  result in a simultaneous reduction of oxy-

of nitric oxide and carbon monoxide.

  The design of the plate-shaped cooling bodies has advantages for the ducting of the secondary air, but is not absolutely necessary. It is also possible to use round-section bars. What is important is that the bars are assembled in such a way.

  sealed with the above mentioned boards to guarantee

  secondary air circulates completely between

  with flames and cooling bars arranged

next to them.

  According to another characteristic of the invention, it may be provided that the boards are made of sheet metal strips or ceramics strips, preferably flat, and

  arranged parallel to the plane of the tubes with multiple nozzles.

  In this way, we arrive at a simple construction

of the burner according to the invention.

  According to another characteristic of the invention, it may be provided that the cooling bodies in the form of plates arranged next to the rows of the gas burners, are

provided with recesses.

  This has the consequence that the secondary air can ar-

  flames in places, allowing for cooling

  punctual burning of flames in specific areas.

  These recesses can have different shapes C '

  so that one or two recesses can be foreseen-

  tending to almost the entire length of the plates But

  it is also possible to equip the cooling plates

  of a series of round holes aligned with the spouts

  In addition, it is also possible to provide rectangular recesses

  gules extending more or less perpendicular to

the longitudinal axis of the plates.

  According to another characteristic of the invention, it can be provided that the cooling plates arranged

  next to the rows of gas burners, are connected between

  by flat ribs placed between spouts, a

  slot being provided between the faces of these ribs,

  the multi-nozzle tube and said tube.

  This makes it possible to ensure a very efficient channeling of the secondary air towards the different flames, which

  guarantees on the one hand their sufficient supply of oxy-

  gene and, on the other hand, efficient cooling of these

  flames and thereby a significant reduction of N Ox.

  In addition, it may be provided to have both sides

  gas beaks several cooling bodies possibly having variable sections and arranged one to

  next to each other or one above the other.

  This results in slits ensuring the pipe e-

  xacts secondary air to specific areas of the flames. It may further be provided that a plate-shaped cooling body is disposed radially at a distance from the gas burners, the longitudinal axis of said body -5-

  being oriented radially with respect to said nozzles.

  The consequence is a particular cooling

  highly effective flames, which is very

the formation of N Ox.

  According to another characteristic of the invention,

  may be provided that a cooling body in the form of

  that is arranged above the gas burners, the longitudinal axis

  dinal said body being substantially parallel to a tangent applied to the section of the multi-nozzle tube,

at the level of said nozzles.

  This solution results in a division of flames

  which extend around the lateral edges of the body

  This results in a very energetic cooling of the flames, the division of which improves

  plus the influx of secondary air to the flames.

  According to another characteristic of the invention,

  may be provided that the cooling bodies are

  at a distance of 4 to 12 mm from the surface of the multi-nozzle tube, the centers of the said bodies being

  on the vector rays of the section of the multilayered tube

  tiples, which touch the limits of the beaks of said tube.

  In this way, the marginal areas of the flames o

  penetrates the oxygen of the air and where there is preferably

  N Ox, are cooled so that the temperature required for the formation of NOX is no longer reached in these areas, while the cooling of the central zone of the flames is largely avoided, which ensures complete combustion in this area This largely removes the

  CO formation and guarantees a high efficiency of the burner.

  According to another characteristic of the invention,

  can be expected that the angle 01 formed by the rays

  the section of the multi-nozzle tube through

  the centers of the sections of cooling bodies, corresponding to

  broadly to the following relation: 4 'b 90 1 a -6- b' being the arc on which the rows of beaks of said tube extend, arranged where appropriate by several beside each other along generators of this tube, and

  indicating the diameter of the multi - nozzle tube.

  It is thus ensured that the flames emerging at the level of the nozzles, where appropriate in several rows along generatrices of the multi-nozzle tube, lick in the zones where the air can penetrate without difficulty the bodies which cool them. cooling

  flames by two bodies in areas where there may be

  see enhanced NO x formation, which is limited in this way. In addition, it can be expected that the number of cooling bodies is greater than that of rows of gas burners used for the formation of main flames, and that the angle d 2 formed by the vector rays of the section of the spout tube multiple, passing through the centers of the sections of cooling bodies, largely corresponds to the following relation: & = 44 k 90 2 dt IT

  k 'being the arc between the centers of two main flames

  neighboring blades, and the diameter of the multi-needle

  ples. This has the effect that marginal areas of all

  the flames are cooled down, which translates into a

  ge emission reduction in NO The heat evacuated by

  cooling bodies may, in this respect, be transmi-

  to the fluid to be heated The existing auxiliary flames

  possibly between the rows of spouts used to form

  of the main flames, and which have a section substantially smaller than that of the beaks where the main flames are born and which, most of the time,

  have an elongated slot shape along the periphery of the tu-

  have multiple beaks, contribute little to the formation of NOX and are cooled in their upper part by

cooling bodies.

  It turned out to be advantageous in this respect that the

  The diameter of the cooling bodies is between 4 and 11 mm.

  By respecting these dimensions, we can be sure that the marginal zones of the flames, which, under the effect of cooling bodies widen a little, are cooled

  enough to prevent the temperature from being exceeded

  necessary for the increased formation of NOX, since the central zones of the flames are hardly affected

  that in these areas the temperature remains sufficiently high

  to ensure almost complete combustion.

  According to another characteristic of the invention,

  it can be provided several cooling bodies by tu-

  be with multiple beaks, arranged on an arc whose center is below the center of the section of said tube,

  The eccentricity amounting to 3 up to 8 mm.

  This results in particularly favorable conditions

  for sufficient cooling of the flame for

avoid the formation of NOX.

  Particularly favorable conditions are obtained.

  the ratio of the diameter of the multi-pipe

  and that of the arc o are aligned the centers of the cooling bodies is between 0.3 and 1.304, and the ratio of the eccentricity vis-à-vis the diameter of said

  body is between 0.3 and 2, and the relationship between the

  centers of two multi-nozzle tubes and the diameter of said tubes is 0.667 to 3.33, the

  produced from these three ratios between 0.05 and 9.

  In this respect, it is particularly advantageous if the

  diameter of the arc carrying the centers of the cooled bodies

sants is the relationship

H = E + 2 * (5 to 12 + G)

  -8- H representing the diameter of the arc joining the centers of the cooling bodies, and E, the diameter of the multi-nozzle tube. By respecting this rule, one obtains, especially if one provides three cooling bodies by multi-nozzle tube, a very fast heat dissipation so as to cool the flame quickly to a temperature

  no longer favoring the formation of NOX and thus preventing

  so effectively the formation of this pollutant.

  A particularly advantageous burner with a view to a reduced No X emission is characterized by a center distance of 40 to 100 mm, a diameter of the multi-nozzle tubes of 30 to 60 mm, a diameter of the arc joining the centers of the cooling bodies from 46 to 1000 mm, and

  a diameter of the cooling bodies from 4 to 10 mm.

  On a burner according to the invention with

  minus a multi-nozzle tube fed with a mixture of gas and

  air and preferably having a diameter of 20 to 60 mm, and provided with radial recesses arranged in rows along with

  minus two generators of said tube, by which the melange

  ge feeding the main flames can flow, one

  can further provide that the cooling bodies are dis-

  placed on two concentric arches with respect to the

multiple beaks.

  In this way, it is guaranteed that the cooling

  This is done in two planes, which guarantees a cooling

  sufficient dissipation even of great flames.

  It has proven particularly advantageous in this context that the distance between the generatrices of the tube

  multiple beaks and cooling bodies the most

  next to each other is 4 to 12 mm.

  According to another characteristic of the invention, it can be provided that, seen with respect to the section of the burner, the cooling bodies located on different arcs, are offset with respect to each other along the periphery of the tube. multiple beaks, and that distance 9 _

  between the generators of said tube closest to that

  the cooling bodies further away, amounts to 15

  up to 20 mm, the offset of the corresponding bodies of pre-

  at half the angle of division of the bodies more

close to the tube.

  It is thus possible to obtain a cooling

  particularly effective flames in their areas

  where there is a strong formation of N O X due to the penetration of air, formation which is prevented by the

  flame cooling in these areas.

  In this connection, it can be expected without inconvenience that

  the vector rays of the multi-nozzle tube section

  ples, which cross the centers of cooling bodies close to said tube, form with the vertical axis of this tube an angle O "from 5 to 400, and that those passing through the

  cooling bodies arranged on the outer arc, one year

gle P from 0 to 200.

  It is thus ensured that the flames, even if they are born on elongated slots essentially along the perimeter of the multi-nozzle tube, are cooled in

their marginal areas.

  In addition, it can be expected that, in view of the

  section of the burner, one of the cooling bodies

  on the vertical axis of the multi-nosed tube, and that another body is placed on the same axis, the minimum distance between the generatrices closest to these two bodies is 3 up to 15 mm.

  Thus, an increased cooling of the flames is

  in areas where two rows of flames meet

  trent, which translates into higher temperatures.

accordingly.

  According to another characteristic of the invention, it can be provided that the cooling bodies arranged

  on different arcs corresponding to the section, are

  killed on common ray vectors of the said section of the -

  tube, and that the distance between the

  ratrices opposed to each other bodies on different

bows rises to 3 up to 15 mm.

  As the flames apply to the cool body

  closest to the multi-needle tube, they are

  amplified in width By the body further away from said tu-

  be, these enlarged flames are inten-

  in their marginal areas, which prevents the

  In this context, it is particularly advantageous to

  that the vector rays of the section of the multilayered tube

  tiples passing through the centers of cooling bodies

  outside, form with the vertical axis of said tube a

from 5 to 400.

  Hereinafter, the invention is described in more detail with the figures of the drawing in support, which show:

  FIG. 1, a first schematic exemplary embodiment

  than a burner according to the invention; Fig 2 is a schematic plan view of the slots of a multi-nozzle tube;

  Fig 3 schematically a burner according to the invention

  with two cooling bodies in section;

  Fig 4 schematically a burner according to the invention

  four cooling bodies in section;

  Fig 5 schematically a burner according to the invention

  with two cooling bodies in section; Fig 6, schematically another burner according to the invention; Fig 7 to 9, sections of different embodiments of burners according to the invention; FIGS. 10 and 11, another embodiment of a

  burner according to the invention, in section and in

axonometric representation;

  Fig 12, a second embodiment of the burn

following them according to the invention;

  Fig 13 to 15, a view of the burner gas burners

  11 - before fig 12; Fig 16 to 26, possible arrangements of the cooling bodies. The tube 1 of the burner according to Fig 1 has at its upper generatrix numerous nozzles 2 through which flows a mixture of a fuel gas

and air, and that is inflamed.

* Next to the flames 3 are arranged, above the tu-

  have multiple beaks 1, two plates 4 which extend

  parallel to said tube and are mounted mainly

  end to delimit the combustion zone.

  Plates 4 are, in this context, disposed of

  so that the ratio between the distance 11 of the inferior edge

  4 of the plates 4 opposite the tube 1 and the width b of the flame 3 at the nozzle of the tube 1 amounts to 0.5

up to 13.4.

  In addition, the ratio of the standard distance 12

  bottom edge opposite the upper edge of the

  than 4 and the distance 1 from the lower edge of the plate 4

  with respect to the tube 1 is between 0.25 and 16.

  The distance y between the plates 4 at their lower edge is chosen so as to exceed 4 to 20

  mm the width of the flame 3 at the nozzle of the tube 1.

  As can be seen from FIG. 1, plates 4, which can

  may be ceramic or metal plates, form

  an angle i with the vertical, the upper edges of the

  your plates getting closer to each other.

  The burner according to FIG. 2 comprises on its tube three rows of orifices 10 which extend along the

  around the multi-needle tube, the 10-group orifices

  in rows A, B and C being aligned on each other

others.

  Between the rows A, B and C there are orifices 10 which have essentially an elongate slot shape and are used to feed the main flames, as well as along the outer edges of the two outer rows A 12 -

  and C, holes 20 are provided through which a

  combustible gas-air mixture can exit the tube 30 to

to create auxiliary flames.

  From FIG. 3 it can be seen that at a distance 'n' from the

  surface of the tube 30, cooling bodies 40 preferably

  ceramics are provided, the distance 'n' being that between the generatrices closest to the tube 30 and

body 40.

  The angle O 1 formed by the vector rays passing through

  the centers of the bodies 40 and which touch the limits ex-

  of the rows A and C of the orifices 10 on the

  turn of the multi-nozzle tube, corresponds to the following relation: 4 b 90 1 = d T bt being the arc along which the orifices 10 arranged next to each other extend in the three rows A,

  B and C on the periphery of the tube 30, and 'd' indicating the di-

meter of the tube 30.

  In this embodiment, only the outer flames are cooled from the outside by the bodies

  , where there is a particular formation of NO,

cooling bodies.

  The exemplary embodiment according to FIG.

  a greater number of bodies 40 which ensure the cooling

  the main flames

  are arranged along the arc defined by the ori-

  10, and the angle '2 formed by the vector rays of the tube 30 passing through the centers of the inner bodies 40 substantially corresponds to the following relation: o = 4, k 90 2 = d 13 - k' being the arc on which extends an orifice 10 of the multi-nozzle tube, and 'd' the diameter of said tube The external cooling bodies are arranged according to the same

principles valid for fig 3.

  As can be seen in FIG. 4, the above formula is not rigorously applied to cooling bodies

  because of the varied distances between the

  these 10 outside and central ones to compensate for these differences.

  the bodies 40 in the middle may have a diameter

  larger than those outside it is indi-

  to have the bodies 40 in the middle each exactly

between two rows of orifices 10.

  The exemplary embodiment according to FIG.

  basically to that of fig 3, to the difference between

  that the cooling bodies 40 are arranged between the rows of orifices 10 so that all the flames are cooled by the effect of said bodies which are arranged exactly between two rows of orifices 10 practically, the embodiment according to FIG. 5 corresponds to that of FIG. 4, with the only difference that the bodies

are removed.

  The distance 'n' between the most productive generators

  bodies 40 and tube 30 is between 4 and 12 mm,

  and the diameter of the cooling bodies, between 4 and 11 mm.

  The multi-nozzle tubes 21 of the exemplary embodiment

  sation according to fig 6 are at a distance D of 100 mm with regard to their centers, the diameter

  E said tubes being 30 to 60 mm.

  At the upper generatrix of the tubes 21 are provided unrepresented nozzles, through which

  flows the fuel mixture to be ignited.

  Above the tube 21 are provided cooling bodies

  sants 22 arranged on an arc whose center is offset from that of the tube 21 of the distance G, downwards, and whose diameter H depends on that of the tube 21 and corresponds to 14 - the relation:

H = E + 2 (5 to 12 + G)

the distance G being from 3 to 8 mm.

  The diameter F of the bodies 22 is advantageously set at 4

up to 10 mm.

  The dimensions of the burner are established elsewhere

  given the relationship between those of different

ments.

  The ratio x between the diameter E of the multi-nozzle tube

  and the diameter H of the arc o are arranged

  22, should correspond to the following relationship

tout: E H

  the value of this report must be between 46 and 100.

  The ratio Y between the distance G and the diameter F of the bodies 22 corresponds to the following relation: G y - F

  the value of this ratio must be between 0.3 and 2.

  The ratio z between the distance D of the centers of the tu-

  21 and the diameter of said tubes corresponds to the relationship

  the value of this ratio to be between 0.667 and

3.333.

  Moreover, the product i of the ratios x y, z must cor-

  respond to the relation: i = x y O z - the value of this product must be between 0.06 and

8,693.

  In the embodiment shown in FIG.

  cooling bodies 31 are arranged on a concentric arc

  relative to the tube 21 which is provided, on either side of the vertical axis of its section, with two rows of orifices extending along generatrices of said tube and

  supplying the main flames Generators

  closest reamers to tube 21 and bodies 31

  at a distance between them of 4 to 12 mm, the dia-

  meter of said bodies rising to 4 up to 12 mm.

  In addition, there are provided cooling bodies 31 'on another arc concentric with respect to the tube 21, these bodies being offset relative to the bodies 31 The bodies 31'

  are essentially arranged on the bisector of the

  vectors passing through the centers of two bodies 31

  drawings. The minimum distance between the generators of the bodies

  31 'and the tube 21 rises to 15 to 20 mm.

  The vector rays passing through the centers of the outer bodies 31 each form with the vertical axis of the

  section of the tube 21 at an angle O from 5 to 400

  passing through the centers of the bodies 311, form each

  together with the vertical axis of the tube section 21 an angle

from 0 to 200.

  In the embodiment shown in FIG. 8, the cooling bodies 31 and 31 'are arranged together on the same vector beams which form with the vertical axis

  of the section of the tube 21 at an angle between 5 and 400. The distances 'e' between the most productive generators

  The lengths of the tube 21 and the bodies 31 are 4 up to 12 mm, and the distances g 'between the respective generatrices.

  cooling bodies 31 and 31 ', at 3 up to 15 mm.

  The embodiment shown in FIG. 9 differs from that of FIG. 7 only in that it is intended to be

  body 31 ", further arranged on the vertical axis of the

  16 - tion of the tube 21 and remote from the body 31, also provided on the vertical axis of the tube 21, the dimension g ", or 3 to 15 mm.

  FIG. 10 shows a section of a burner

  According to the invention, several multi-nozzle tubes 1 are arranged parallel to one another, which channel a combustible gas-air mixture and are provided with nozzles 2 through which the mixture leaves to feed the flames 3, the nozzles being essentially provided along

  of the upper generatrix of each of the tubes 1.

  Above the tubes 1 and on both sides of the axis

  main vertical section of said tubes are preferably

  seen cooling bodies 4 in the form of plates made of a strip of sheet metal, which form with the vertical axis of

flames 3 a very sharp angle.

  The bodies 4 disposed on either side of the rows of flames of adjacent tubes 1, are interconnected by walls 5 which prevent secondary air from circulating.

  upwardly between the bodies 4 connected in this way,

  that secondary air can only flow along

  cooling elements 4 arranged on both sides of the dif-

several rows of flames.

  This is how secondary air cools flames

  3, which largely prevents the formation of N Ox In addition, the secondary air enters the flames, which

  results in complete combustion despite the cooling

  dissement, which also largely prevents the

of CO.

  In the embodiment shown in FIGS. 10 and 11, the walls 5 are connected flat sheet metal strips

  to the bodies 4 over their entire length and arranged parallel

  at the level of multi-needle tubes 1.

  In the embodiment shown in FIG. 12, the bodies 4 are connected to each other, as in the example according to FIGS. 10 and 11, but the bodies 4 adjoined to

  a row of beaks or flames, are by nerves

  17 - res 44 essentially standing that are arranged between

  different beaks and separated from them by slits.

  As can be seen from Figs 13, 14 and 15, the bodies

  4 may be provided with recesses 41 extending

  along said bodies, or recesses 42 disposed more or less perpendicularly to their longitudinal axis

  and more or less in front of the beaks, or recesses 43 es-

  sensually circular, as it follows from fig 15.

  FIG. 16 shows another way of disposing a cooling body 4 placed radially with respect to the beaks of

so that the flames enclose it.

  The embodiment according to FIG. 17 differs

  from that of fig 16 only because the body

  4 is disposed more or less tangentially to the tube 1 so that the flames are split and lick the lateral edges of said body FIGS. 18 to 26 show

  different embodiments of the burner according to

  According to the invention, on either side of the row of beaks of the tube 1 are provided several bodies 4 (FIG.

  22), or body combinations 4 and 40, the secondary air

  re able to reach the flames in places through

slots provided between these bodies.

  With the exception of the examples of realization following the

  24 and 25, the cooling bodies 4 and 40 are

  essentially one above the other,

  say that in Figs 24 and 25, they are essential

next to each other.

  R eve N dicatio N s 1 Burner with at least one multi-nozzle tube, fed with a combustible mixture and provided with radial nozzles arranged essentially along a generatrix of the tube, cooling bodies being provided at a certain distance and beyond above said tube, and more or less parallel to it, characterized in that the cooling bodies (4) are arranged on either side of the rows of the beaks, and thus limiting laterally the area occupied by the

flames (3).

  2 burner according to claim 1, characterized in that the ratio between the distance (11) of the lower edges of the cooling bodies designed in the form of plates (4) vis-à-vis the highest generatrix of the multi-nozzle tube (1) and the width of the flames at the point of contact with the spout of the tube (1) is 0.5

up to 13.4.

  Burner according to Claim 1 or 2, characterized in that the ratio between the length (12) of the end face of the plates (4) and the distance (11) of the lower edges of the plates (4) vis-à-vis of the highest generator of the multi-nozzle tube (1) is 0.25

up to 16.

  Burner according to one of Claims 1 to 3,

  characterized in that the plates (4) are arranged at an angle to the vertical, the ratio between the free distance (x) of the plates (4) of a multi-nozzle tube (1) in their upper part and the free distance (y) of the plates (4) in their part

  lower is from 1.036 to 10.238.

  Burner according to one of Claims 1 to 4,

  characterized in that the free distance (y) between the plates (4) of a multi-nozzle tube (1) in their lower part corresponds to the width of the flames (3) at the point of contact with the nozzle, plus a supplement of 4 to mm.

  Burner according to one of Claims 1 to 5,

  characterized in that the cooling bodies (4) arranged on different sides of two adjacent multi-nozzle tubes (1), and having a preferably rectangular cross-section, are interconnected by a clipboard

(5) united.

  Burner according to one of Claims 1 to 6,

  characterized in that the boards (5) are made of sheet metal strips or ceramic strips, preferably flat, and arranged parallel to the plane of the

multi-needle tubes (1).

  Burner according to one of Claims 1 to 7,

  characterized by the fact that the cooling bodies (4) in the form of plates arranged next to the rows of the beaks

  with gas, are provided with recesses (41, 42, 43).

  Burner according to one of Claims 1 to 8,

  characterized in that the cooling bodies (4) in the form of plates arranged next to the rows of the gas burners, are interconnected by flat ribs (44) placed between spouts, a slot being provided between the faces of these ribs looking at the tube with multiple beaks

(1) and said tube.

  Burner according to Claim 1, characterized in that on both sides of the gas burners, a plurality of cooling bodies (4, 40) optionally having sections

  are arranged side by side or one beside the other

above each other.

M 2677110

  Burner according to Claim 1, characterized in that each plate-shaped cooling body (4) is arranged radially at a certain distance from the gas nibs, the longitudinal axis of said body (4) being oriented

  radially with respect to said nozzles.

  Burner according to Claim 1, characterized in that each plate-shaped cooling body (4) is arranged above the gas nibs, the longitudinal axis of said body (4) being substantially parallel to a tangent applied to the nozzle. section of the tube with multiple nozzles

(1), at the level of said nozzles.

  Burner according to Claim 1, characterized in that the cooling bodies (40), preferably ceramic, are arranged at a distance of 4 to 12 mm from the surface of the multi-nozzle tube (30), the centers of said bodies ( 40) being located on vector rays of the multi-nozzle tube section (30), which

  touch the limits of the nozzles (19) of the tube (30).

  Burner according to Claim 13, characterized in that the angle θ 1 formed by the vector rays of the section of the multi-nozzle tube (30) passing through the centers of the sections of the cooling bodies (40) corresponds approximately to the following relation: 4 xbx 90 dtb 'being the arc on which the rows (A, B, C) of spouts (10) of the tube (30) extend, arranged where appropriate by several adjacent to one another the other along generatrices of this tube (30), and indicating the diameter of the tube

multiple beaks (30).

  Burner according to claim 13, characterized in that the number of the cooling bodies (40) is greater than that of the rows (A, B, C) of gas nozzles (10) of the tube (30), serving for the formation of main flames, and that the angle i 2 formed by the vector rays of the section of the multi-nozzle tube (30), passing through the centers of the sections of the cooling bodies (40), corresponds approximately to the following relation: 2 = 4 xkx 90 drk 'being the arc on which extends a beak (10) of the tube

  (30), and the diameter of the multi-nozzle tube.

  Burner according to Claim 13 or 14, characterized in that the diameter of the cooling bodies (40) is

between 4 and 11 mm.

  Burner according to Claim 1, characterized in that a plurality of cooling bodies (22) are provided by multiple nozzle tubes (21) and arranged on an arc whose center is below the center of the tube section ( 21), the eccentricity amounting to 3 up to 8 mm. Burner according to Claim 17, characterized in that the ratio (x) between the diameter (E) of the multi-nozzle tube (21) and the diameter (H) of the arc o are aligned with the centers of the cooling bodies ( 22) is between 0.3 and 1.304, and that the ratio (y) between the eccentricity (G) and the diameter (F) of the bodies (22) is between 0.3 and 2, and the ratio ( z) between the distance (D) of the centers of two multi-nozzle tubes (21) and the diameter (E) of the tubes (21) is 0.667 to 3.33, the product (i) of these three ratios between 0.05 and 9. 19 Burner according to claim 17 or 18, characterized in that the diameter (H) of the arc carrying the centers of the cooling bodies (22) corresponds to the relationship

H = E + 2 x (5 to 12 + G).

  Burner according to one of Claims 1 to 19,

  characterized in that the distance (D) from the centers of the multi-nozzle tubes (21) is 40 to mm, the diameter (E) of the tubes (21) to 30 to mm, the diameter (H) of the arc joining the centers of the cooling bodies (22), to 46 up to 1000 mm, and the diameter (F) of the cooling bodies (22), to 4 up to mm. Burner according to Claim 1, with at least one multi-nozzle tube fed with a gas-air mixture and preferably having a diameter of 20 to 60 mm, and provided with radial recesses arranged in rows along at least two generatrices. of said tube, through which the mixture feeding the main flames can flow, characterized in that the cooling bodies (31, 31 ') are arranged on two concentric arcs by

  compared to the multi-nozzle tube (21).

  22 burner according to claim 21, characterized in that the distance between the generatrices of the multi-nozzle tube (21) and cooling bodies (31) the most

  close to 4 to 12 mm.

  Burner according to Claim 21 or 22, characterized in that the cooling bodies (31, 31 ') situated on different arcs, with respect to the section of the burner, are offset relative to one another by along the periphery of the multi-nozzle tube (21), and that the distance between the generatrices of the tube (21) closest to those of the cooling bodies (31 ') farther away is 15 to 20 mm, the bodies (31 ') situated on the outer arc being arranged on the bisector of the rays passing through the centers of the bodies (31) located on

the inner bow.

  24 burner according to claim 23, characterized in that the vector rays of the section of the multi-nozzle tube (21), which pass through the centers of the cooling bodies (31) close to the tube (21), form with the vertical axis of this tube an angle o L of 5 & 400, and that those passing through the cooling bodies (31 ') arranged

  on the outer arc, an angle b from 0 to 200.

  Burner according to claims 21 to 24, characterized

  in that one of the cooling bodies (31) arranged on the inner arc lies on the vertical axis of the multi-nozzle tube (21), and that another cooling body (31 ") is disposed on this same axis, the minimum distance between the generatrices closest to these two bodies (31, 31 ") provided on the vertical axis of the section of the tube (21), amounts to 3 to 15 mm (FIG. Burner according to Claim 21 or 22, characterized in that the cooling bodies (31, 31 ') arranged on different arcs corresponding to the section, are located on common vector spokes of said section of the multi-nozzle tube ( 21), and that the distance between the generatrices opposite to each other of the bodies (31,

  31 ') on different arches is 3 to 15 mm.

  27 Burner according to Claim 26, characterized in that the vector rays of the section of the multi-nozzle tube (21) passing through the centers of the external cooling bodies (31 ') form with the axis

  vertical of said tube an angle (5 to 400.

-AT