EP2232141B1 - Surface-combustion cylindrical burner provided with a device for stabilising the pressure and the flow of a gaseous mixture, and method - Google Patents

Description

The present invention relates to the supply of combustible gas mixture, for example air / natural gas mixture, air / propane, air / butane, air / biogas, or air / fuel vaporized, a cylindrical burner surface combustion.

More specifically, it relates to a pressure and flow stabilizing device for such a gas burner, a gas burner equipped with this stabilizer device, and a method for stabilizing the pressure and the flow of the gas mixture feeding the burner.

A cylindrical surface-burning gas burner comprises a perforated cylindrical wall pierced with a multitude of small orifices, a discoid bottom wall and an inlet opening, through which a pre-mixed combustible gas mixture (premix) is introduced into the burner, for example by means of a fan or a turbine.

Usually, the cylindrical wall is a perforated stainless steel sheet, the orifices being circular holes and / or slots of very small section.

The invention is also applicable, however, to grid-like walls or as a layer of porous material resistant to high temperatures (for example woven fibers made of refractory material).

The combustible gas is distributed inside the burner and escapes radially through the orifices of the cylindrical wall; the burner being lit, the outer face of the wall acts as a combustion surface, each orifice generating a radial flame of greater or lesser height, depending on the area of its section and the gas flow.

This type of burner is particularly suitable for equipping a boiler, for domestic or industrial use, provided with one or more tubes (circular section or other) surrounding the combustion surface.

One or more fluids to be heated circulates in this (these) tube (s) which is (are) licked (s) by the hot gases from the combustion surface.

Different configurations are possible, in particular comprising a sheet of rectilinear tubes parallel to the generators of the burner (see for example the document FR-A-2,476,808 ), or comprising one or more bundles of tubes wound in a helix (see for example the documents WO 94/16272 , Figure 18, or EP-A-1,813,882 ). The document EP 1 538 395 discloses a cylindrical burner having the features mentioned in the preamble of claim 1.

The invention relates more particularly to the stabilization of the pressure and the flow rate of the gas mixture inside the burner, so as to obtain a complete combustion and evenly distributed over the entire cylindrical combustion surface of the burner, with a uniform flame height for optimal performance while reducing emissions of carbon monoxide (CO) and carbon dioxide (CO ₂ ).

The quality and the hygiene of the surface combustion obtained by this type of burner depend on several parameters, in particular on the dimension (section of passage) of the orifices made in the cylindrical wall, and of their mutual spacing (rate of openwork). perforated wall).

Depending on the length and diameter of the cylindrical, it is difficult to ensure a steady flow of gas over the entire length of the burner.

However, the uniformity of the gas flow over the entire combustion surface conditions the combustion height and its regularity over the entire surface, on which the emission of CO and CO ₂ depends.

In order to improve this uniformity, it has already been proposed to double the cylindrical wall by internally providing the burner with a cylindrical envelope (second wall), also perforated, with a diameter slightly smaller than that of the wall which serves combustion surface, these two walls being coaxial. This arrangement has the effect of increasing the level of pressure required for the exhaust gas mixture, it must firstly pass through the orifices of the inner envelope to occupy the annular space between the two walls, then the orifices of the outer wall which acts as a combustion surface. Thus the combustion ports are fed at a relatively even pressure over the entire surface of the outer wall.

This solution is not fully satisfactory insofar as the uniformity obtained is not perfect and because the addition of the inner envelope significantly increases the weight and cost of the burner. In addition, the presence of the inner casing induces a significant pressure drop of the gas flow circulating in the burner.

The good distribution of the gaseous premix inside the burner is largely related to the flow of the gas flow just before it enters the burner, as we will explain now by referring to the Figures 1 to 3 .

In these figures, there is shown a conventional surface-type gas combustion burner 1, comprising a cylindrical perforated wall 2 of axis X- X ' (For example horizontal), crossed by a multitude of small holes 20, a sealed discoid bottom 3, and a circular inlet opening 10, through which a combustible gas mixture is introduced inside the burner 1.

This is a mixture previously made of a fuel with an oxidant, in particular a liquefied petroleum gas, a natural gas, a biogas (resulting from a fermentation), or even vaporized fuel oil, mixed with air or oxygen in an adequate proportion to ensure correct and complete combustion.

As is well known, this fuel premix, designated G, is supplied to the burner by means of a fan V.

The combustion surface is constituted by the outer face of the wall 2, on which the flames are formed, referenced F.

The combustion is generally initiated by an igniter (not shown) located near this surface.

To improve the distribution of the pressure inside the burner 1 and, correlatively, the quality of the combustion, it is known to insert a sleeve between the outlet of the fan V and the inlet 10 of the burner.

In the configuration illustrated on the figure 1 the outlet mouth of the fan is circular and has the same diameter as the inlet 10 of the burner. The sleeve M used is cylindrical also having this diameter, and the assembly is mounted coaxially along X-X '.

Thus the gas flow, symbolized by the arrows f is regular, and the burner 1 is fed homogeneously, which allows to obtain a good distribution of pressures and flow rates in the burner, resulting in a relatively high flame height h constant over the entire combustion surface.

On many boiler models, it is not possible, especially for reasons of space, to place the fan in the axis of the burner.

This is the case for the configuration represented on the figure 2 , in which the axis of the fan is offset relative to the latter. The connecting sleeve M ' here has end portions bent at right angles, so that the flow of gas f' entering the burner has a deflected and disturbed trajectory, generating an irregular flame height F ' .

In the configuration shown on the figure 3 , the connecting sleeve M " is provided with a safety valve comprising a flap A, hinged at the top, the function of which is to prevent back-flue gas from burner to the fan when it is stopped. This is useful especially when several devices are connected to the same chimney.

The valve is closed when the shutter, under the effect of its own weight, is in the vertical position A ₀ shown in phantom in the figure.

Its opening angle is automatically dependent on the operating speed, the flow of gas supplied by the fan counteracting the weight of the flap A more or less depending on the flow.

The flow f " passing under the shutter to then enter the burner is here also deviated (bias) and disturbed, generating an irregular flame height F" .

It is difficult in many configurations and operating modes of the boilers, especially with variable flow operating modes for power modulation, to obtain a uniform distribution of flame heights on the combustion surface.

The difficulty is even greater in the case of remote positioning of the fan relative to the burner ( figure 2 ) or the presence of a flap at the burner inlet ( figure 3 ).

The object of the invention is to solve these problems by proposing a burner comprising a pressure and flow-stabilizing device of simple design, without moving parts, which is light and inexpensive, with practically no pressure drop, suitable for be placed at the burner inlet in order to appreciably improve the distribution of the gas mixture inside the burner and thus ensure a homogeneous supply of all the orifices of the combustion surface, by generating a flame height constant on all this surface.

As already mentioned, this pressure and flow stabilizing device is intended to equip a gas burner having a perforated cylindrical wall acting as a combustion surface, a bottom wall and an inlet opening, through which a combustible gas mixture is introduced inside the burner.

According to the invention, the device consists of a grid adapted to be positioned inside said inlet opening, and comprising a central ring surrounded by a series of deflecting blades, this grid being thus shaped that it authorizes the free passage of the central portion of the gas mixture flow entering the burner through the central ring, while said deflector blades generate a swirling movement of the peripheral portion of this flow entering the burner from the outside of the central ring.

Thus, the burner is fed simultaneously with two gaseous flows of different configurations, namely an external cyclonic vortex which moves along an approximately helical path towards the bottom wall of the burner, and a central undisturbed flow, or little disturbed, which also moves to the bottom of the burner while relaxing inside the cyclone.

Surprisingly, such an arrangement ensures a regular pressure over the entire surface of the burner, both along its circumference and along its length.

The patent document EP-1,538,395 relates to a cylindrical gas burner internally provided with a device for reducing the acoustic resonance phenomena and, correlatively, the burner noises.

This device comprises parallel or "cross" partitions, which prevent any swirling movement of the gas mixture feeding the burner, which thwarts the homogenization and good distribution of this mixture, contrary to the desired objective.

The German utility model DE 9013114 U , meanwhile, describes a disc intended to equip a burner oil or gas. This disk is provided with a central opening through which the fuel (fuel) and a first part of the air (oxidizer) pass, as well as a series of radial slots which are crossed by the other part of the necessary air. to combustion. This document does not specify which form of burner this disc is associated, nor fortiori, that the disc is positioned inside the inlet opening of this burner.

Its function is not to improve the distribution of an already constituted gaseous premix inside the burner but rather to perfect this premix from two flows of different nature, namely a central flow formed of fuel and of air and a peripheral flow formed only of air.

It is not excluded that said mixture feeds the burner via a double bent cuff such as that designated M ' on the figure 2 , or a sleeve provided with a safety valve such as that designated M " on the figure 3 of the present patent application, with the resulting disadvantages as discussed above.

• l'anneau central est circulaire, et est coaxial à la paroi cylindrique perforée (lorsque le dispositif est monté sur le brûleur) ;
• lesdites pales s'étendent radialement par rapport à l'axe de la paroi cylindrique perforée (lorsque le dispositif est monté sur le brûleur), avec une répartition angulaire régulière ;
• le nombre de pales est compris entre 6 et 30, et avantageusement entre 11 et 25 ;
• lesdites pales sont des lamelles planes, toutes identiques et de largeur constante, qui sont inclinées suivant la direction longitudinale, leur plan formant un angle aigu par rapport à l'axe de la paroi cylindrique perforé ;
• ledit angle a une valeur comprise entre 15 et 45 °, de préférence de l'ordre de 30° ;
• lesdites pales sont solidaires de l'anneau central ;
• ladite grille comprend un anneau extérieur circulaire, dont les pales sont solidaires, apte à être emmanché et immobilisé dans l'ouverture d'entrée du brûleur ;
• l'anneau central est un manchon dont la longueur est sensiblement égale à la dimension axiale des pales (solution adaptée à un brûleur de faible à moyenne longueur) ;
• l'anneau central est un manchon dont la longueur est supérieure à la dimension axiale des pales (solution adaptée à un brûleur de grande longueur).

According to other advantageous features that are possible, but not limiting, of the invention:

• the central ring is circular, and is coaxial with the perforated cylindrical wall (when the device is mounted on the burner);
• said blades extend radially with respect to the axis of the perforated cylindrical wall (when the device is mounted on the burner), with a regular angular distribution;
• the number of blades is between 6 and 30, and advantageously between 11 and 25;
• said blades are flat slats, all identical and of constant width, which are inclined in the longitudinal direction, their plane forming an acute angle with respect to the axis of the perforated cylindrical wall;
• said angle has a value between 15 and 45 °, preferably of the order of 30 °;
• said blades are integral with the central ring;
• said grid comprises a circular outer ring, whose blades are integral, adapted to be fitted and immobilized in the burner inlet opening;
• the central ring is a sleeve whose length is substantially equal to the axial dimension of the blades (suitable solution for a burner of low to medium length);
• the central ring is a sleeve whose length is greater than the axial dimension of the blades (solution adapted to a burner of great length).

The invention relates to a cylindrical burner with surface combustion equipped with a pressure-stabilizing device as described above.

Finally, it also relates to a method for stabilizing the pressure and the flow rate of a combustible gas mixture feeding a gas burner, the latter having an inlet opening, a perforated cylindrical wall acting as a combustion surface, and a bottom wall, this process consisting in dividing the gaseous mixture entering the burner into two distinct streams, namely a central flow with undisturbed flow, or slightly disturbed, substantially laminar, able to reach said bottom wall while gradually widening, and a swirling flow with approximately helical trajectory surrounding the central flow.

Other characteristics and advantages of the invention will appear on reading the following description of a preferred embodiment of the invention.

• la figure 4 est une vue en perspective d'un premier mode de réalisation possible du dispositif stabilisateur de l'invention ;
• la figure 5 est une vue de face, à plus grande échelle, du dispositif de la figure 4 ;
• la figure 6 est une vue de côté, en coupe, du même dispositif, le plan de coupe étant référencé VI -VI sur la figure 5 ;
• les figures 7 et 8 représentent un deuxième mode de réalisation possible du dispositif stabilisateur de l'invention, ces vues étant similaires, respectivement, aux figures 4 et 6 du premier mode de réalisation ;
• la figure 9 représente un troisième mode de réalisation possible du dispositif stabilisateur de l'invention, cette vue étant similaire à la figure 4 du premier mode de réalisation ;
• la figure 10 est une coupe axiale d'un brûleur pourvu d'un dispositif stabilisateur conforme au premier mode de réalisation ;
• la figure 11 est une vue analogue à la figure 10, destinée à illustrer le fonctionnement du dispositif en montrant comment se fait la répartition des flux gazeux à l'intérieur du brûleur ;
• la figure 12 est une vue en perspective, et en coupe, similaire à la figure 11 ;
• la figure 13 est une vue analogue à la figure 11, mais avec un brûleur de plus grande longueur, pourvu d'un dispositif stabilisateur conforme au second mode de réalisation.

This description is made with reference to the accompanying drawings in which:

• the figure 4 is a perspective view of a first possible embodiment of the stabilizer device of the invention;
• the figure 5 is a front view, on a larger scale, of the device of the figure 4 ;
• the figure 6 is a side view, in section, of the same device, the section plane being referenced VI -VI on the figure 5 ;
• the Figures 7 and 8 represent a second possible embodiment of the stabilizing device of the invention, these views being similar, respectively, to Figures 4 and 6 of the first embodiment;
• the figure 9 represents a third possible embodiment of the stabilizing device of the invention, this view being similar to the figure 4 of the first embodiment;
• the figure 10 is an axial section of a burner provided with a stabilizing device according to the first embodiment;
• the figure 11 is a view similar to the figure 10 , intended to illustrate the operation of the device by showing how the gas flow is distributed inside the burner;
• the figure 12 is a perspective view, and in section, similar to the figure 11 ;
• the figure 13 is a view similar to the figure 11 but with a longer burner provided with a stabilizing device according to the second embodiment.

The device represented on the Figures 4 to 6 consists of a grid, for example of thin stainless steel sheet.

This grid 4a is composed of a pair of concentric rings, one central 5a, the other outer 7, shaped cylindrical sleeves of short length, common axis X-X ', as well as a series of blades 6.

These extend radially with respect to the X-X ' axis with a regular angular distribution.

In the example shown, the grid comprises 12 blades, distributed at 30 ° all around the central ring.

They are fixed at their ends, for example by welding, to each of the two sleeves 5a and 7.

As can be seen on the figure 6 both sleeves and blades are thin and their axial dimension e is identical.

The outer diameter of the ring 7 is chosen to correspond to the inside diameter of the cylindrical wall of the burner to be equipped, so that the grid can be inserted and maintained without play in the burner inlet opening, coaxially with it.

These blades 6, all identical, are flat blades of constant width.

They are inclined in the longitudinal direction, so as to form an acute angle, designated α on the figure 6 , with respect to the axis X-X '. As an indication, this angle has a value of the order of 30 °.

The central ring 5a defines a cylindrical channel 8, of axis X-X ', allowing the free passage of gases.

The spaces between blades 6 define an annular peripheral passageway 9 for the gases.

The device which is the subject of the second embodiment represented on the Figures 7 and 8 consists of a gate 4b which is different from the gate 4a which has just been described in that the length i of its central sleeve, referenced 5b, is significantly larger than the axial dimension e common to the blades 6 and the 7. As will be seen later, with reference to the figure 13 , the portion of this sleeve 5b which protrudes from the general plane of the grid is intended to penetrate inside the burner.

The device which is the subject of the third embodiment represented on the figure 9 consists of a gate 4c which differs from the gate 4a in that it does not have an outer ring.

The blades 6 are intended to be positioned and apply directly against the cylindrical inner face of the burner inlet opening. These blades therefore have a length such that their outer edge fits into a cylindrical envelope (fictional) whose diameter corresponds to that of this inner face.

Note also that the number of blades 6 is twice that of the previous devices, since it is 24, spread at 15 ° angle accordingly.

The burner represents it on the figure 10 is of the same type as that described above with reference to Figures 1 to 3 .

A stabilizing device 4b according to the first embodiment described above is fitted axially into the inlet opening 10 of the burner and is retained therein, for example under the effect of the simple friction due to a certain tightening between the external face. of the ring 7 and the inner face of the mouth of the cylindrical wall 2.

Advantageously, the ring 10 is provided with a flange 70 forming a stop, which limits its penetration inside the burner body.

The figures 11 and 12 illustrate the mode of action of the device.

The flow of gas G discharged by the fan and arriving at the burner inlet la must pass through the grid of the stabilizer 4a.

It is then subdivided into two distinct flow parts, namely a central part which passes through the channel 8 delimited by the central ring 5a, and an outer part which passes through the space 9 formed between the blades 6.

On the figure 11 the dashed line represents the fictional envelope Ea separating these two parts.

The central flow, symbolized by the arrows X, is a regular or even laminar flow, generally trajectory in translation along X-X ' towards the bottom 3. However, the gaseous mass tends to flare, in the form of cone, then "in trumpet", as shown by the outline of the envelope Ea.

The external flow, symbolized by the arrows Y, follows a swirling trajectory, in a helix, at a high speed, around the central flow, this trajectory combining an axial translation movement and a rotational movement (twisting) which is printed to it by the inclination of the deflecting blades 6.

The external flow surrounds the central stream over almost its entire length (upstream side).

In a relatively surprising manner, the combination of these two flows ensures a regular distribution of the flow rate and the pressure of the gas inside the burner, over its entire length and over its entire periphery (over 360 °).

In practice, it appears that the combustion orifices 20 of the upstream portion of the burner (on the side of the inlet opening 10) are essentially fed with gas supplied by the swirling external flow whereas on the contrary the combustion orifices the downstream end portion of the burner (near the bottom 3) are essentially fed with gas supplied by the undisturbed central flow.

As one moves from upstream to downstream, the amount of gas from the external flow decreases, while that from the central flow increases, the sum of the two quantities remaining substantially constant. The internal cyclonic movement of the burner further promotes a good distribution of flow and pressure, so that in the end we obtain a flame height F of constant height over the entire combustion surface.

This remarkable result is obtained even when the gas flow that reaches the burner is deflected and / or inclined, in particular as a result of the presence in upstream of it with an angled cuff of the kind shown on the figure 2 , a valve of the kind shown on the figure 3 , or a flow control valve supplied to the burner.

The pressure loss resulting from the presence of the device at the burner inlet is negligible.

The dimensions of the stabilizer device must naturally be adapted to the structure and dimensions of the burner.

As an indication, the burner la just described has a perforated wall 2 made of stainless steel sheet whose thickness is 0.3 mm.

The rate of perforation of the wall (ratio of the area of the perforations and the total area of the perforated wall) is of the order of 30%.

Its length and internal diameter, respectively designated La and Da on the figure 10 are respectively 160 mm and 70 mm.

The stabilizing device 4a can also be made of a thin sheet of stainless steel.

The outer ring 7 has a diameter of 70 mm with a functional tolerance allowing it to fit without play, or even with a certain tightening, into the burner inlet opening.

The central ring 5a has a diameter of 24 mm.

The axial dimension e of the device is 10 mm.

The burner 1b shown on the figure 13 is similar to the burner 1a with the exception of its length Lb which is larger.

As an indication, Lb = 240 mm

Its diameter Db = 70 mm.

As already stated, the stabilizing device 4b, meanwhile, is identical to the device 4a, except for the sleeve constituting the central ring 5b, whose length i is substantially greater than e.

As an indication, i = 25 mm (while e = 10 mm).

As we see on the figure 13 , this sleeve 5b has the effect of channeling the central flow so that it diverges less rapidly than the central flow of the first embodiment, so that it can reach the bottom wall 3, farther from the opening than previously.

The envelope Eb which separates the central stream from the external cyclone flow flares more progressively downstream, inside the burner 1b, than the envelope Ea inside the burner 1a.

The operating mode of the two stabilizers, however, is similar, and generates a uniform distribution of gas flow and pressure, resulting in a regular flame height and optimal combustion hygiene.

In the embodiments described above, the inlet opening 10 of the burner is circular and its diameter is the same as that of the cylindrical perforated wall.

These features are not mandatory.

In addition, the stabilizer device could be shaped so as to cap (from the outside) the inlet mouth of the burner instead of fitting inside.

Claims (13)

1. A cylindrical combustion surface gas burner including a perforated cylindrical wall (2) acting as a combustion surface, a bottom wall (3) and an inlet opening (10) through which a combustible gas mixture is introduced inside the burner (1), characterized in that it comprises a pressure and flow rate stabilizing device which comprises a grid (4a, 4b, 4c) including a central ring (5a, 5b) surrounded by a series of diverting vanes (6), this grid (4a, 4b, 4c) being adapted to be positioned inside said inlet opening (10), such that the central ring (5a, 5b) of X-X' axis be coaxial with the perforated cylindrical wall (2) of the X-X' axis,
   said central ring (5a, 5b) allowing free passage of the central portion of the gas mixture flow penetrating the burner, while said diverting vanes (6) generate a vortex movement of the peripheral portion of this flow penetrating the burner (1) from the outside of the central ring (5a, 5b).
2. The burner according to claim 1, characterized in that the central ring (5a, 5b) is circular.
3. The burner according to claim 1 or claim 2, characterized in that said vanes (6) extend radially relatively to the axis (X, X') of the perforated cylindrical wall (2) with a regular angular distribution.
4. The burner according to claim 3, characterized in that the number of vanes (6) is comprised between 6 and 30.
5. The burner according to claim 4, characterized in that the number of vanes is comprised between 11 and 25.
6. The burner according to one of the claims 3 to 5, characterized in that said vanes (6) are planar lamellas, all identical and with constant width, which are tilted in the longitudinal direction, their plane forming an acute angle (α) relatively to the axis (X-X') of the perforated cylindrical wall (2).
7. The burner according to claim 6, characterized in that said angle (α) has a value comprised between 15 and 45°.
8. The burner according to claim 7, characterized in that said angle (α) has a value of the order of 30°.
9. The burner according to any one of claims 1 to 8, characterized in that said vanes (6) are integral with the central ring (5a, 5b).
10. The burner according to any one of claims 1 to 9, characterized in that said grid (4a, 4b) comprises an outer circular ring (7), the vanes (6) are integral therewith, capable of being fitted and immobilized into the inlet opening (10) of the burner (1).
11. The burner according to claim 10, characterized in that the central ring (5a) is a sleeve, the length of which is substantially equal to the axial dimension (e) of the vanes (6).
12. The burner according to claim 10, characterized in that the central ring (5b) is a sleeve, the length (i) of which is greater than the axial dimension (e) of the vanes (6).
13. A method for stabilizing the pressure and flow rate of a combustible gas mixture feeding a gas burner (1) with a combustion surface, the latter including an inlet opening (10), a perforated cylindrical wall (2) acting as a combustion surface, and a bottom wall (3), characterized in that the gas mixture penetrating the burner (1) is divided into two distinct flows, i.e. a central flow with non-perturbed, or not very perturbed flow, substantially laminar, capable of reaching said bottom wall (3) while flaring out gradually, and a vortex flow with an approximately helical trajectory surrounding the central flow.

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