阅读说明：本技术 燃烧器 (Burner with a burner head ) 是由 里卡尔多·潘科里尼 于 2015-02-11 设计创作，主要内容包括：本发明描述的是一种燃烧器(1)包括头部(2),在该头部(2)限定燃烧发生的燃烧区域(3)；第一燃料入口(4),其中有用于调节供应的燃料数量的入口阀门(5)；第二入口(7),用于使助燃物在燃烧区域(3)的方向上延伸,并且将助燃物馈送入燃烧区域(3)；第二入口(7)包括用于运送助燃物的运送导管(9),调节装置(8)沿导管(9)放置。运送导管(9)沿开始于助燃物的各自入口端(30)的各自延伸轴(29)延伸；第二入口(7)包括用于偏转进入的助燃物的偏转器元件(31),使助燃物在相对于运送导管(9)的延伸轴的径向方向上进入。(The invention describes a burner (1) comprising a head (2), in which head (2) a combustion zone (3) is defined in which combustion takes place; a first fuel inlet (4) in which there is an inlet valve (5) for adjusting the amount of fuel supplied; a second inlet (7) for extending the comburent in the direction of the combustion zone (3) and feeding the comburent into the combustion zone (3); the second inlet (7) comprises a conveying duct (9) for conveying comburent, the regulating device (8) being placed along the duct (9). The conveying ducts (9) extend along respective extension axes (29) starting from respective inlet ends (30) of the comburent; the second inlet (7) comprises a deflector element (31) for deflecting the incoming comburent, so that it enters in a radial direction with respect to the extension axis of the conveying duct (9).)

1. Burner (1), comprising:

a head (2) in which a combustion zone (3) in which combustion takes place is defined;

a first fuel inlet (4) in which there is an inlet valve (5) for adjusting the amount of fuel supplied; said first fuel inlet (4) is defined by a conduit for conveying fuel (6), along which conduit said inlet valve (5) is placed; the conduit for conveying the fuel (6) extends in the direction of the combustion zone (3) for feeding the fuel; the inlet valve (5) intercepts the fuel and is configured for adjusting the amount of fuel in transit by directing the first fuel inlet (4) towards the combustion zone (3);

a second inlet (7) for extending the comburent in the direction of the combustion zone (3) and feeding the comburent into the combustion zone (3); said second inlet (7) comprising adjusting means (8) for adjusting the quantity of comburent fed to the combustion zone (3); said second inlet (7) comprising a conveying duct (9) for conveying comburent, said regulating device (8) being placed along the duct (9); a conveying duct (9) for conveying comburent extends in the direction of the combustion zone (3) for feeding comburent;

wherein the conveying conduits (9) extend along respective extension axes (29) starting from respective inlet ends (30) of the comburent; the second inlet (7) comprises a deflector element (31) for deflecting the incoming comburent, configured to cause the entry of comburent in a radial direction with respect to the extension axis of the conveying duct (9).

2. Burner (1) according to claim 1, wherein said deflector element (31) is shaped in the form of a cap, located at said inlet end (30) of the comburent, and has a single internal section greater than the section of said inlet end, so as to form a cylindrical air inlet zone (32) between said conveying duct (9) and said deflector element (31).

3. Burner (1) according to claim 1 or 2, wherein said deflector element (31) has at least one inlet channel (33) for said comburent, extending radially with respect to said extension axis (29) and located along said conveying duct (9) away from said inlet end (30).

4. Burner (1) according to any one of the preceding claims, wherein said deflector element (31) defines an initial portion of the second inlet 7 for the entry of comburent.

5. Burner (1) according to any one of the preceding claims, wherein said deflector element (31) defines a path for feeding the comburent and defines a reversal of the feeding direction of the comburent at the inlet end (30) of the conveying duct (9).

6. Burner (1) according to any one of the preceding claims, when depending on claim 2, wherein said inlet channel (33) extends along a crown located on a cap-like deflector element (31) and is defined by a plurality of through holes.

7. Burner (1) according to claim 6, wherein the other structure of the deflector element (31) is closed at the other end.

8. Burner (1) according to any one of the preceding claims, further comprising a control device (11) for controlling the combustion, the control device (11) comprising first measuring means (12) for measuring the flow rate (Vg) of the fuel supplied to the burner (1), the first measuring means (12) being inserted along the first inlet (4) and inside a conduit for conveying the fuel (6).

9. Burner (1) according to any one of the preceding claims, further comprising a control device (11) for controlling the combustion, the control device (11) comprising a second measuring device (13) for measuring the flow rate (Va) of the comburent supplied to the burner (1), the second measuring device (13) being inserted along the second inlet (7) and being placed along the conveying duct (9) for conveying the comburent.

10. Burner (1) according to claim 9, wherein said second measuring means (13) are located inside a deflector element (31) between said inlet channel (33) and said inlet end (30).

11. Burner (1) according to claim 10, wherein said second measuring means (13) comprise a sensor (34) configured to measure the flow rate of said comburent by the venturi effect.

12. Burner (1) according to claim 10, wherein said second measuring means (13) comprise a conveyor (17B) having a narrow portion in the feeding direction (18) of the fuel; the carrier (17B) is located inside a deflector element (31).

13. Burner (1) according to any one of the preceding claims, wherein each conveyor (17) is located inside a respective conveyor duct (6, 9) and is connected to the respective conveyor duct (6, 9) by means of a bracket (24), said bracket (24) being connected between said conveyor (17) and said duct so as to maintain said conveyor (17) in a central position with respect to a transverse section of said inlet (4, 7).

14. Burner (1) according to any one of the preceding claims, wherein a second measuring device (13) is positioned between the inlet channel (33) and the inlet end (30) so that part of the comburent flow passes from the cylindrical zone (32) to the inlet end (30) by the venturi effect, while hitting the sensor (34).

15. Burner (1) according to claim 14, wherein the second measuring means (13) are connected to the outer surface of the conveying duct, but inside the cylindrical zone (32); said conveyor (17B) coincides with the direction of entry of the comburent from the inlet channel (33) to the inlet end of the conveying duct (9), in such a way that the second measuring means (13) minimally affect the movement of the comburent entering from the inlet channel (33).

Technical Field

The present invention relates to a device for controlling the combustion of a burner, a burner comprising such a control device and a method of controlling the combustion of a burner.

Preferably, the invention defines controlling the mixing between the fuel and the comburent to control the combustion in the burner.

The invention relates to burners used both in the domestic sector (for example for heating) and in the industrial sector (for example for producing general heat, for ovens, for heating air, etc.).

More specifically, the invention is used in non-premixed burners, i.e. in those burners where the comburent and the fuel are mixed directly at the head of the burner.

Background

According to the prior art, the burner comprises an inlet duct for fuel (generally gaseous fuel) and an inlet duct for comburent (generally air). These inlet ducts merge in the combustion zone where the burner head is located. In this way, the mixture of comburent and fuel performs combustion for heating (when initiated by the ignition spark), for example liquid.

Typically, the burner comprises a valve for regulating the fuel gas, placed along the inlet conduit of the fuel, for regulating the quantity of gas supplied to the head. Similarly, the burner also comprises an opening with variable cross section, placed along the comburent air inlet conduit, for regulating the quantity of air supplied to the head.

Furthermore, two techniques are known for controlling the valve to adjust the gas and air inlet opening cross-section.

According to a first prior art, both the movement of the gas regulating valve and the air inlet opening cross-section are of the mechanical type. In other words, the adjustment of the valve and of the inlet section is achieved by the movement of the respective movable cams, which are configured on the basis of the air/gas ratio curve predetermined during the test phase. The movement of the cam is controlled by a control unit as a function of measured temperature and pressure values (e.g. on the steam of a boiler). Moreover, the movement of the cam requires manual adjustment during installation by a trained installer to configure the air/gas ratio curve based on the operating power of the burners in the system to achieve the optimum excess air value during the air/gas conditioning operation.

According to a second prior art, the control of the gas regulating valve and of the cross section of the air inlet opening is of the electronic type. In this case, the adjustment of the valve and of the inlet section is performed electronically on the basis of a predetermined air/gas ratio curve stored in the storage unit. Furthermore, the adjustment is performed as a function of the value of the combustion gas measured by a specific sensor for measuring the O contained in the fumes₂And/or CO. In this case, the control unit 16 is configured to maintain the combustion at an optimum level according to the excess air index curve. Furthermore, the control unit is configured to automatically adjust the burner to a high safety curve (O) when the excess air index reaches too low₂At least 1% greater than the corresponding value on the air/gas ratio curve).

In any case, during installation, a trained operator must manually create a ratio air/gas curve stored in the storage unit, gradually increase the opening of the gas and observe O₂And/or tendency of CO.

However, these prior art techniques have several disadvantages.

A first drawback linked to the fact is that, in both cases, at least a first intervention must be made by a trained operator during installation in order to set/adjust the air/gas ratio curve. Since proper (or incorrect) operation of the burner is dependent on the adjustment, the operation must be present by a trained operator.

A second drawback, related to the first, is that once the adjustment is performed by a trained operator, the operation of the first burner is based on the air/gas ratio curve that has been set. Thus, changes in air and/or gas parameters or changes in operating combustor components (e.g., associated with wear of mechanical components over time) may result in the combustor operating in a non-optimal state because the air/gas profile settings are no longer applicable.

In practice, the burner is controlled by means of a suitable smoke analysis instrument and by a trained technician during the first opening of the burner, and not during the burner operation, by constructing an air/gas ratio curve. Thus, variations in the fuel or comburent parameters may cause defective combustion (even if it falls within the safety parameters of the combustion gases), or it may not reach the level of power required.

Alternatively, it is necessary to require regular intervention by a trained operator to adjust the burner. However, the latter solution has even inherent drawbacks due to the number of calls (which may be long) made by the operator and the relative cost of the intervention.

Disclosure of Invention

In this situation, the object of the present invention is to provide a device for controlling the combustion of a burner, a burner and a method of controlling the combustion of a burner which overcome the above-mentioned drawbacks.

More specifically, it is an object of the present invention to provide a burner with an optimized oxidant inlet path.

Furthermore, it is an object of the present invention to provide a burner with means for controlling the combustion during the operation of the burner, which allows maintaining an optimal air/gas ratio.

It is another object of the present invention to provide an apparatus for controlling combustion that allows automatic control of the air/gas ratio during operation of the burner.

Finally, another object of the present invention is to provide a device for controlling the combustion which allows automatic control of the air/gas ratio during the operation of the burner as a function of the variation of the parameters of the fuel and of the comburent.

The object indicated is substantially achieved by a device for controlling the combustion of a burner, a burner and a method for controlling the combustion of a burner as described in the claims herein. Further characteristics and advantages of the present invention will become more apparent with reference to non-limiting and non-exclusive preferred embodiments of an apparatus for controlling the combustion of a burner, a burner and a method for controlling the combustion of a burner as illustrated in the accompanying drawings.

Drawings

Fig. 1 shows a cross-sectional axial view of a burner according to the invention.

Fig. 2 shows a sectional side view of the burner in fig. 1.

Fig. 3 shows a block schematic diagram for controlling the combustion of a burner according to the invention.

Fig. 4 shows a cross-sectional isometric view of a first detail of the burner of fig. 1.

Fig. 5 shows a cross-sectional side view of the first detail depicted in fig. 4.

Fig. 6 shows a cross-sectional isometric view of a second detail of the burner of fig. 1.

Fig. 7 shows a cross-sectional side view of the second detail depicted in fig. 6.

Figure 8 shows a cross-sectional isometric view of a variation of the first detail depicted in figure 4.

Fig. 9 shows an enlarged cross-sectional axial side view of the variation in fig. 8.

Fig. 10 shows a side view of an alternative embodiment of the burner of fig. 1.

FIG. 11 illustrates an isometric view of an alternative embodiment of the combustor of FIG. 10.

FIG. 12 shows a cross-sectional isometric view of a detail of an alternative embodiment of the combustor in FIG. 11, an

FIG. 13 shows an enlarged cross-sectional isometric view of a detail of the alternative embodiment in FIG. 12.

Detailed Description

With reference to the above figures, numeral 1 indicates as a whole a burner according to the invention.

Preferably, the burner 1 comprises a head 2, in which head 2 a combustion zone 3 is defined in which the combustion takes place.

More preferably, the burner 1 is of the non-premixed type (mixing between fuel and comburent takes place directly on the head 2 instead of before).

More specifically, the burner 1 comprises a first fuel inlet 4 in which there is an inlet valve 5 for adjusting the amount of fuel supplied. Preferably, the first inlet 4 is defined by a duct for conveying the fuel 6, along which an inlet valve 5 is placed. The conduit for carrying the fuel 6 extends in the direction of the combustion zone 3 for feeding the fuel.

The inlet valve 5 intercepts the fuel and is configured to regulate the amount of fuel in transit by directing the first inlet 4 towards the combustion zone 3. The inlet valve 5 is of a known type and will not be described in detail below.

It should be noted that the fuel is a fluid and may be of the liquid or gaseous type. Preferably, the fuel comprises methane or GPL or biogas or a mixture of these or other substances which are still capable of being combusted without being explicitly mentioned here.

Furthermore, the burner 1 comprises a second inlet 7 for extending the comburent in the direction of the combustion zone 3 and feeding the comburent into the combustion zone 3. In more detail, the second inlet 7 comprises means for adjusting the quantity of comburent fed to the combustion zone.

Preferably, the second inlet 7 comprises a duct 9 for conveying comburent, the regulating device 8 being placed along the duct 9. A conduit 9 for conveying comburent extends in the direction of the combustion zone 3 for feeding comburent.

The conveying ducts 9 extend along respective extension axes 29 starting from respective inlet ends 30 of the comburent.

More specifically, in the embodiment illustrated in fig. 10-13, the second inlet 7 comprises an element 31 for deflecting the entering comburent, configured to enter the comburent in a radial direction with respect to the extension axis of the conveying duct 9.

The deflector element 31 is shaped in the form of a cap and is located at the inlet end 30 of the comburent. In other words, the second inlet 7 comprises the conveying duct 9 and the deflector element 31. The deflector element 3 defines an initial portion of the second inlet 7 for the entry of comburent.

Furthermore, the deflector element 31 has a respective internal cross-section greater than that of the inlet end 30, thereby forming a cylindrical air inlet region 32 between the duct of the second inlet 7 and the deflector element 31. The deflector element 31 defines a path for feeding the comburent and defines the reversal of the feeding direction of the comburent at the inlet end 30 of the conveying duct 9.

The deflector element 31 has at least one inlet channel 33 for comburent extending radially with respect to the axis of extension 29 and is located along the duct at a position distant from the inlet end 30. Fig. 12 shows that the inlet channel 33 extends along a crown located on the cap-like deflector element 31 and is defined by a plurality of through holes. On the other hand, the other structure of the deflector element 31 is closed.

In the embodiment illustrated in figures 2, 12 and 13, the regulating device 8 has an opening 35 with an adjustable section for regulating the quantity of comburent supplied. Preferably, the adjustment means 8 have one or more movable shutters 36 with an inclination adjustable with respect to the direction of propagation of the comburent as a function of the quantity of comburent fed.

It should be noted that the burner comprises, advantageously, a fan 27 for feeding air (not visible in the figures) in the direction of the head 2 for feeding air into the combustion zone 3. Advantageously, the burner comprises a duct for feeding air, which extends from the fan 27 for feeding air to the head 2, thereby directing the air into the burner region 3. The fan for feeding air is driven by a motor 28, preferably an electric motor (shown in fig. 1 and 2).

In an alternative embodiment not shown in the figures, the adjustment means 8 comprise a module for adjusting the number of revolutions (rpm) of the fan 27 for feeding air, and an opening 35 with an adjustable section. In practice, the fan 27 for feeding air is of the adjustable output type, with which the quantity of air pushed towards the burner 3 is varied. Preferably, the module for adjusting the number of revolutions of the fan 27 is configured to act on the electric feeder of the fan 27 (generally defined by an inverter).

As already mentioned in part, the burner 1 has a combustion zone 3 where the first inlet 4 and the second inlet 7 merge and where the fuel and the comburent mix to allow combustion to occur.

Furthermore, the burner 1 comprises a pressure-stabilizing valve 10 placed along the first inlet 4 upstream of the combustion zone 3. Preferably, the pressure-stabilizing valve 10 is placed along the conduit for transporting the fuel 6 and is configured to keep the fuel pressure constant between the stabilizing valve 10 and the inlet valve 5. The stabilizer valve 10 is of a known type and will not be described in detail below.

Furthermore, the burner 1 comprises a device 11 for controlling the combustion, which is also an object of the present invention.

More specifically, the control device 11 comprises first means 12 for measuring the flow rate Vg of the fuel supplied to the burner 1.

A first measuring device 12 is inserted along the first inlet 4. In other words, the first measuring device 12 is located inside the conduit for transporting the fuel 6.

Preferably, the first measurement device 12 includes a sensor 34 configured to measure the fuel flow rate Vg. More preferably, the sensor 34 of the first measuring device 12 is of the instantaneous measuring type. In other words, the sensor is designed to instantaneously measure a value with respect to the fuel flow rate Vg. Furthermore, the sensor 34 of the first measuring device 12 is advantageously located in the centre of the conduit for transporting the fuel 6.

Fig. 4 and 5 show an embodiment of the first measuring device 12. In more detail, the first measuring device 12 comprises a conveyor 17 having a narrow portion in the feeding direction 18 of the fuel. In more detail, the conveyor 17 comprises a wide end 19 located in the intake zone of the fuel and a narrow end 20 located downstream of the wide end 19 in the feeding direction 18 of the fuel. The narrow end 20 defines a duct 21 inside for the passage of the fuel, wherein the velocity of the fuel increases due to the narrowing of the passage portion.

The measuring sensor 34 of the conveyor 17 extends transversely to the feeding direction of the comburent and projects inside the narrow end 20. More specifically, the measurement sensor 34 is configured to directly measure the flow rate of the fuel. Preferably, the measurement sensor 34 is a hot film or hot wire type flow meter.

It should be noted that the carriers 17 are located inside the first inlet 4 and define an internal passage section smaller than the section of the first inlet 4, whereby most of the fuel passes outside the respective carrier 17. In this way, the fraction of fuel affected by the presence of the carrier and entering the carrier is minimal with respect to the fuel passing inside the first inlet 4.

More specifically, the carrier 17 occupies a reduced portion of the space inside the first inlet 4, and a portion of the fuel inside the first inlet 4 enters inside the carrier 17, and a portion (mostly) passes outside the carrier 17 between the carrier 17 and the first inlet 4.

It should be noted that the first inlet 4 is defined by a duct inside which a conveyor 17 is present. Preferably, the conveyor 17 is located in an intermediate position according to both the radial to the catheter direction and the longitudinal direction.

In an alternative embodiment not shown in the drawings, instead of the wide portion 19, the conveyor 17 comprises elements of different sizes based on the desired velocity gradient of the fluid in the immediate vicinity of the sensor 34.

More specifically, the sensor 34 of the first measuring device (shown in fig. 8 and 9) is located at the narrow end 20 inside the hole 22, which extends transversely to the feed direction 18 of the fuel. Preferably, the sensor 34 is placed transversely to the feed direction 18 of the fuel and projects in a cantilever manner inside the channel duct 21, thereby being exposed in the channel of the fuel and measuring the flow rate.

Furthermore, the conveyor 17 has a final re-widening 23 at its portion furthest from the previously defined wide portion 19.

Furthermore, fig. 4 and 5 show the first measuring device 12 comprising a support 24, the support 24 being configured to keep the carrier 17 in a central position with respect to the transverse section of the first inlet 4 (fig. 1), whereby the flow of fuel striking the carrier 17 is uniformly concentrated at the inlet, which is defined by the wide portion 19, and the turbulence effect due to the roughness of the inner wall of the duct, although very limited, is perceived as small as possible. More specifically, the bracket 24 may have various configurations. Preferably, with the sensor 34 for the fuel, the support 24 is formed by a wing projecting from the inner wall of the first inlet 4.

Fig. 8 and 9 show that the carrier 17 is mounted inside the duct of the first inlet 4 and is connected to the first inlet 4 by means of a bracket 24. Preferably, in fig. 8 and 9, the support 24 incorporates the sensor 34 and its associated parts diametrically opposite each other are flanged (flanged) in order to support two portions of the pipe which extend differently in a symmetrical direction with respect to each other. This allows self-support while centering the carrier 17 inside the conduit of the first inlet 4.

Furthermore, the apparatus 11 comprises second means 13 for measuring the flow rate Va of the comburent supplied to the burner 1.

A second measuring device 13 is inserted along the second inlet 7.

In a first embodiment, illustrated in figures 1 and 2, a second measuring device 13 is placed along the duct 9 for conveying the comburent.

In a second embodiment illustrated in fig. 10-13, the second measuring device 13 is located inside a deflector device 31 as described in detail below.

In any case, the second measuring device 13 comprises a sensor 34 configured to measure the flow rate Va of the comburent. More preferably, the sensor 34 of the second measuring device 13 is of the instantaneous measuring type. In other words, the sensor 34 is designed to instantaneously measure a value relative to the flow rate Va of the comburent. As shown in fig. 1, the sensor 34 of the second measuring device 13 is advantageously positioned in the centre of the duct 9 for conveying comburent.

As mentioned above, fig. 6 and 7 show a preferred embodiment of the second measuring device 13 for the sensor 34 of the first measuring device 12. In more detail, the second measuring device 13 comprises (for the sake of simplicity, the same numbers indicating the first measuring device 12 will be used) a conveyor 17 having a narrow portion along the feeding direction of the comburent. In more detail, the conveyor 17 comprises a wide end 19 located in the intake zone of the comburent and a narrow end 20 located downstream of the wide end 19 in the feeding direction 19 of the comburent. The narrow end 20 defines the inside of a conduit 21 for the comburent to pass through, the velocity of which increases due to the narrow part of the passage section.

The measuring sensor 34 of the conveyor 17 extends transversely to the feeding direction of the comburent and projects inside the narrow end 20. More specifically, the measurement sensor 34 is configured to directly measure the flow rate of the comburent. Preferably, the measurement sensor 34 is a hot film or hot wire type flow meter.

It should be noted that the conveyors 17 are located inside the second inlet 7 and define an internal passage section smaller than the section of the second inlet 7, whereby the majority of the comburent passes outside the respective conveyor 17. In this way, the fraction of fuel affected by the presence of the carrier and entering the carrier is minimal with respect to the fuel passing inside the second inlet 7.

More specifically, the conveyor 17 occupies a reduced portion of the space inside the second inlet 7, and a portion of the comburent passing through the second inlet 7 enters inside the conveyor 17, and a portion (mostly) passes outside the conveyor 17 between the conveyor 17 and the second inlet 7.

In an alternative embodiment not shown in the drawings, instead of the wide portion 19, the conveyor 17 comprises elements of different sizes based on the desired velocity gradient of the fluid in the immediate vicinity of the sensor 34.

More specifically, the sensor 34 (not shown in the figures) of the second measuring device 13 is located inside the hole 22 of the narrow end 20, which extends transversely to the feeding direction 18 of the comburent. Preferably, the sensor 34 is placed transversely to the feeding direction 18 of the comburent and projects in a cantilever manner inside the passage conduit 21, thereby being exposed in the passage of the comburent and measuring the flow rate.

Furthermore, the conveyor 17 has a final re-widening 23 at its portion furthest from the previously defined wide portion 19.

It should be noted that in the first embodiment illustrated in fig. 1 and 2, the carrier 17 is located inside the carrier conduit 9.

Furthermore, fig. 6 and 7 show a second measuring device 13 comprising a support 24, the support 24 being configured to keep the conveyor 17 in a central position with respect to the transverse section of the second inlet 7 (fig. 1), so that the flow of comburent hitting the conveyor 17 is uniformly concentrated at the inlet defined by the wide portion 19, and as little turbulence effect as possible, though very limited, is felt due to the roughness of the inner wall of the duct. More specifically, the bracket 24 may have various configurations. Preferably, with the sensor 34 for comburent, the support 24 comprises a ring structure 25 positioned in contact with the inner wall of the second inlet 7 and a plurality of radial tabs 26 extending between the ring structure 25 and the conveyor 7.

In the second embodiment illustrated in fig. 10-13, the carrier 17 is located inside the deflector element 31. More specifically, as shown in fig. 12 and 13, the second measuring device 13 is located between the inlet channel 13 and the inlet end 30. In this way, part of the comburent flow passes from the cylindrical zone 32 through the inlet end 30, hitting the sensor 34 at the same time. Preferably, the second measuring device 13 is connected to the outer surface of the conveying duct, but inside the cylindrical area 32. The conveyor 17 coincides with the direction of entry of the comburent from the inlet channel 33 to the inlet end of the conveying duct 9. In this way, the second measuring device 13 minimally influences the movement of the comburent entering from the inlet channel 33.

As shown in fig. 12 and 13, the burner 1 comprises a circular element 37, which circular element 37 extends around the conveying duct and has a plurality of through holes 38, which through holes 38 are positioned at the wide end 19 of the conveyor 17B, so that the flow of the combustion agent passes through said through holes 38 and the wide end 19 with a minimum portion of the total combustion agent passing in the cylindrical zone 32.

It should be noted that the first flow rate measuring device 12 and the second flow rate measuring device 13 are configured to generate respective measurement signals. The measurement signal is preferably an electrical type signal expressed in Volts (Volts) or amperes (Amps).

Furthermore, the apparatus 11 comprises a control unit 16 operatively connected to the first measuring device 12 and the second measuring device 13 and configured to receive the respective measuring signals.

In other words, the control unit 16 is configured to measure the flow rate Va of comburent and the flow rate Vg of fuel as a function of the content of the respective measurement signals.

In an alternative embodiment not shown in the figures, the first measuring device 12 and/or the second measuring device 13 comprise at least two conveyors 17, inside each of which a respective sensor 34 is inserted. Advantageously, the presence of the conveyors 17 makes it possible to obtain greater safety in the operation of the control device 11 if at least one of the sensors is missing or the air flow in at least one of the conveyors 17 is blocked. In this case, the control unit 16 is configured to receive several measurement signals from the measuring devices 12, 13 of the same type (air or gas) and compare them with each other, thereby checking any damage/malfunction of the sensor 34 or checking any blockage of the conveyor.

Additionally or alternatively, the control unit 16 is configured to compare measurement signals received from the measurement devices 12, 13 of the same type (air or gas) and compare them to each other, thereby adjusting (e.g. averaging) the measured flow rate values to increase the accuracy of the measurement.

In any case, the conveyors 17 of the same type of measuring device 12, 13 (air or gas) are located in different areas, in order to measure the respective flow rates at different points.

A device for measuring the flow rate Vg of the fuel is installed between the stabilizing valve 10 and the valve 5.

It should be noted that the sensor 34 of the first measuring device 12 and the sensor 34 of the second measuring device 13 are configured to measure the flow rate or other quantity related to the flow rate (by a mathematical formula), such as velocity.

Furthermore, the apparatus 11 comprises first operator means 14 for controlling the opening of the inlet valve 5 as a function of the quantity of fuel supplied to the burner 1. In other words, the first operator device 14 of the valve allows to control the amount of fuel passing through the first inlet 4. In other words, the first operator device 14 of the valve allows to control the fuel quantity of the duct for conveying the fuel 6.

It should also be noted that the first operator device 14 is mechanically connected to the valve 5 for moving it. Preferably, as shown in fig. 3, the first operator device 14 includes a servo control.

Moreover, the plant 11 comprises second operator means 15 of the device 8 for adjusting the quantity of comburent to control the passage of comburent. In other words, the second operator device 15 of the valve allows to control the quantity of comburent passing through the second inlet 7. In other words, the second operator device 15 of the valve allows to control the quantity of comburent passing in the delivery duct 9.

Preferably, the second operator device 15 is mechanically connected to a movable shutter 36 which is tiltable so as to be moved. Preferably, as shown in fig. 3, the second operator device 15 comprises a servo control.

If the means 8 for adjusting the quantity of comburent comprise a module for adjusting the number of revolutions (rpm) of the fan 27 feeding the air, the second operator device 15 is connected to a feeder, preferably an inverter, of the fan 27 for adjusting the air flow generated. More specifically, the operator device 15 is configured to act on (act on) the shutter 35 and the fan 27 as a function of a predetermined curve having the relationship between the inflowing comburent flow and the opening of the second inlet 7.

In other words, the operator device 15 is connected between the supply of the fan 27 and the shutter 36, thereby controlling the air flow generated by the fan 27 and the opening of the shutter 36. Preferably, the control device 15 comprises a control unit. In this case, the control unit also controls and manages an operator device 14 for adjusting the quantity of fuel supplied to the burner 1.

And in the preferred embodiment, the operator device 15 is configured to first control the opening of the shutter 36 (until reaching almost full opening), and then control the increase in the number of revolutions of the fan 27, thereby optimally supplying air. Alternatively, the ratio between the number of revolutions of the mode 27 and the opening of the shutter 36 may be controlled by different modes in relation to the setting of the control unit 16.

The control unit 16 is operatively connected to the first operator device 14 and to the second operator device 15 as a function of the values measured by the first measuring device 12 and the second measuring device 13.

In other words, the control unit is configured to receive the measurement signal and to generate control signals for controlling the first and second operator devices 14, 15, respectively.

More specifically, the opening 35 having an adjustable cross-section is configured to generate an opening signal indicative of the movement of the opening. The control unit 16 is configured to receive the opening signal, to compare the content of the opening signal with the trend of the comburent flow rate Va measured by the second measuring device 13, in order to check whether the comburent flow rate coincides with the movement of the opening 35 with adjustable section. In other words, if the opening signal indicates that the section of the opening is increasing and that the comburent flow rate is also increasing in turn, this means that the comburent flow rate is coincident with the movement of the opening 35 with adjustable section, otherwise it is not. Conversely, if the opening signal indicates that the section of the opening 35 is decreasing and that the comburent flow rate is also decreasing in turn, this means that the comburent flow rate is coincident with the movement of the opening 35 with adjustable section.

In other words, if the opening signal indicates that the section of the opening 35 is increasing (or decreasing) and that the comburent flow rate is decreasing (or increasing or remaining constant), this means that the comburent flow rate is not coincident with the movement of the opening 35 with adjustable section.

If the comburent flow rate does not coincide with the movement of the opening 35 with adjustable section, the control unit 16 is configured to generate an alarm signal.

Similar to what has just been described, the inlet valve 5 is configured to generate an opening signal indicative of the opening movement of the valve. More specifically, the control unit 16 is configured to receive the opening signal, compare the content of the opening signal with the trend of the flow rate Vg of the fuel measured by the first measuring device 12, and thereby check whether the fuel flow rate coincides with the movement of the valve 5. In other words, if the opening signal indicates that the valve is opening and the fuel flow rate is in turn increasing, it means that the fuel flow rate is consistent with the movement of the valve. Conversely, if the opening signal indicates that the valve 5 is closing and the fuel flow rate is in turn decreasing, this means that the fuel flow rate coincides with the movement of the valve 5.

On the other hand, if the opening signal indicates that the valve is opening (or closing) and the fuel flow rate is decreasing (or increasing or remaining constant), then this means that the fuel flow rate is not consistent with the movement of the valve.

If the fuel flow rate is not consistent with the movement of the valve 5, the control unit 16 is configured to generate an alarm signal.

It should be noted that the second means 13 for measuring the flow rate of the comburent are located upstream of the regulating means 8 of the feed direction of the comburent.

In more detail, the second means 13 for measuring the flow rate of the comburent are located upstream of the fan 27 in the feeding direction of the comburent.

In this way, the measuring device 13 is minimally affected by the turbulence generated by the fan 27 and by the movement of the adjusting device 8. Also, it is easier to remove if necessary to replace the measuring device.

Similarly, the first means 12 for measuring the fuel flow rate are also located upstream of the inlet valve 5 in the feed direction of the fuel, whereby they are minimally affected by the movement of the inlet valve 5.

According to the invention, the control unit 16 is configured to perform a first feedback check to control the first operator device 14 and a second feedback check to control the second operator device 15. During the first feedback check the control unit 16 is configured to:

generating an ideal flow rate value Vgr for the fuel (corresponding to a value expressed in volts or amperes) as a function of a predetermined thermal power value Wr for the burner 1 (function k (Wr));

measuring the flow rate (corresponding to a value expressed in volts or amperes) of the fuel fed to the burner 1 through the first measuring means 12;

-comparing the measured fuel flow rate value Vg with the ideal flow rate value Vgr and generating a corresponding offset value eg as a function of the difference between the measured flow rate value Vg and the ideal flow rate value Vgr.

-controlling (function G (eg)) the first operator means 14 to adjust the opening of the inlet valve 5 as a function of the generated offset value eg, whereby the measured fuel flow rate value approaches the ideal fuel flow rate value Vgr.

It should be noted that the step of generating the ideal flow rate Vgr of the fuel as a function of the predetermined thermal power value Wr is performed by making use of a power/flow rate equation providing a relationship between a plurality of thermal power values Wr selectable by an operator (or provided by the modulator R (tc, pc) based on the energy requirements of the plant) and the corresponding ideal fuel flow rate Vgr. The predetermined heat power value Wr is preferably calculated by a modulator R (tc, pc) (also forming part of the burner) as a function of the values measured by means installed in the burner (for example, for boilers, the temperature value of water tc or the pressure value of steam pc are measured on the basis of the heat power value Wr calculated by the modulator). In any case, the thermal power value Wr depends on the heat quantity requested by the user. Preferably, the R (tc, pc) modulator is implemented by the control device 1.

Furthermore, the control unit 16 comprises a memory module which stores power/flow rate equations for a predetermined thermal power depending on the type of fuel used.

Furthermore, the ideal flow rate Vgr is preferably an electrical quantity.

Furthermore, the comparison of the measured instantaneous fuel flow rate value Vg with the ideal flow rate Vgr is performed using a suitable comparison module.

Furthermore, it should be noted that the control unit 16 is configured (function G (eg)) to increase the opening of the inlet valve 5 if the ideal flow rate Vgr is greater than the measured flow rate value Vg, and to decrease the opening of the inlet valve 5 if the ideal flow rate Vgr is less than the measured flow rate value Vg.

As mentioned, the control unit 16 is configured to perform the second feedback contact to the second operator device 15 by performing the following operations:

measuring the flow rate Va (corresponding to a value expressed in volts or amperes) of the comburent fed to the burner 1 by the second measuring device 13;

-generating an ideal flow rate value Var (corresponding to a value expressed in volts or amperes) for the comburent as a function of the measured fuel flow rate, from a predetermined curve of values h (Vg) representing the relation between the ideal comburent flow rate Var and the fuel flow rate Vg.

-comparing the measured comburent flow rate Va with the ideal comburent flow rate value Var and generating an offset value ea as a function of the difference between the measured flow rate value Va and the ideal flow rate value Var.

-controlling (function F (eg)) the second operator device 15 to adjust the flow rate of comburent into the second inlet 7 as a function of the generated offset value ea, whereby the comburent flow rate value Va measured approaches the ideal comburent flow rate value Var.

It should be noted that the step of generating the ideal flow rate Var of comburent as a function of the measured fuel flow rate is carried out by using a predetermined curve (function h (Vg)) representing the ratio of the ideal comburent flow rate Var to the fuel flow rate Vg. The curve of values is preferably stored in a memory module of the control unit 16.

Furthermore, the desired flow rate value Var of the comburent is preferably an electrical quantity.

Moreover, the comparison of the measured comburent flow rate value Va with the ideal flow rate Var is carried out using a suitable comparison module.

Moreover, it should be noted that the control unit 16 is configured (function F (eg)) to increase the passage of comburent if the ideal flow rate value Var is greater than the measured flow rate value Va and to decrease the passage of comburent if the ideal flow rate value Var is less than the measured flow rate value Va.

Advantageously, the first and second feedback checks control whether the combustion is maintained within optimum limits, making them close to the ideal fuel flow rate value Vg for the addition of fuel and close to the ideal flow rate value Va for the comburent for the addition of air. In this way, the system adjusts itself so that the combustion remains constant as the flow rate value Vg of the fuel and/or the flow rate value Va of the comburent vary.

In fact, at the same time, the first feedback check tends to bring the fuel quantity value Vg close to the pre-calculated optimal flow rate value as a function of the set power Wr, and the second feedback check tends to bring the comburent flow rate value Va close to the calculated optimal flow rate value as a function of the measured fuel flow rate value. In this way, the system self-regulates. Preferably, each feedback check defines a proportional-integral-derivative (PID) type of control.

Furthermore, the device 11 comprises a first temperature sensor at the first inlet 4 configured to measure the temperature of the fuel. More specifically, the control unit 16 is connected to the first temperature sensor to receive the temperature signal T1 and is configured to determine the ideal flow rate Vgr of the fuel as a function of the measured temperature value T1.

In other words, the measured temperature value T1 is taken into account when generating the ideal flow rate value Vgr for fuel. More specifically, the control unit 16 modifies the ideal flow rate value Vgr of the fuel as a function of the measured temperature value T1 according to a predetermined mathematical expression.

Furthermore, the device 11 comprises a second temperature sensor located at the second inlet 7, configured to measure the temperature of the comburent. More specifically, the control unit 16 is connected to the second temperature sensor to receive the temperature signal T2 and is configured to determine the ideal flow rate Var of comburent as a function of the measured temperature value T2.

In other words, the measured temperature value T2 is taken into account when generating the ideal flow rate value Var of comburent. More specifically, the control unit 16 modifies the ideal flow rate value Var of the comburent as a function of the measured temperature value T2 according to a predetermined mathematical expression.

In addition to the temperature sensor, the device 11 may comprise a pressure sensor Pr located at the first inlet 4, configured to measure the pressure Pr of the fuel. The control unit 16 is configured to determine an ideal flow rate value Vgr of the fuel as a function of the measured pressure value Pr. In other words, the measured pressure value Pr is taken into account when generating the ideal flow rate value Vgr for the fuel. More specifically, the control unit 16 modifies the ideal flow rate value Vgr of the fuel as a function of the measured pressure value Pr according to a predetermined mathematical expression.

Furthermore, the device 11 may comprise a pressure sensor Pa located at the second inlet 7, configured to measure the pressure Pa of the incoming comburent. The control unit 16 is configured to determine an ideal flow rate value Var of the comburent as a function of the measured pressure value Pa.

In other words, the measurement of the atmospheric pressure value Ph is taken into account when generating the ideal flow rate value Var of comburent. More specifically, the control unit 16 modifies the ideal flow rate value Var of the comburent as a function of the measured pressure value Pr of the comburent according to a predetermined mathematical expression.

Furthermore, the apparatus 11 may comprise an atmospheric pressure sensor Ph located at the second inlet 7, configured to measure the external atmospheric pressure Ph. The control unit 16 is configured to determine an ideal flow rate value Vgr of the fuel and/or an ideal flow rate value Var of the comburent as a function of the measured atmospheric pressure value Ph.

In other words, the measured atmospheric pressure value Ph may also be taken into account when generating the ideal flow rate value for fuel Vgr and/or the ideal flow rate value for comburent Var. More specifically, the control unit 16 modifies the ideal flow rate value Vgr of the fuel and/or the ideal flow rate value Var of the comburent as a function of the measured atmospheric pressure value Pr according to a predetermined mathematical expression.

Furthermore, the apparatus 11 may comprise a first humidity sensor Uma located at the second inlet 7, configured to measure the humidity of the comburent. The control unit 16 is configured to determine the desired flow rate value Var of the comburent as a function of the measured humidity value Uma. In other words, the measured humidity value Uma may be taken into account when generating the desired flow rate value Var of the comburent. More specifically, the control unit 16 modifies the ideal flow rate value Var of the comburent as a function of the measured humidity value Uma according to a predetermined mathematical expression.

Furthermore, the device 11 may comprise a second humidity sensor Umg located at the first inlet 4, configured to measure the humidity of the fuel. The control unit 16 is configured to determine an ideal flow rate value Vgr of the fuel as a function of the measured humidity value Umg. In other words, the measured humidity value Umg may also be taken into account when generating the ideal flow rate value Vgr for the fuel. More specifically, the control unit 16 modifies the ideal flow rate value Vgr of the fuel as a function of the measured humidity value Umg according to a predetermined mathematical expression.

Furthermore, the control unit 16 is further configured to:

-defining a ratio C (Va/Vg) between the measured comburent flow rate value Va and the measured fuel flow rate value Vg;

-comparing the ratio C (Va/Vg) with a predetermined range of safe combustion values;

-if the ratio C (Va/Vg) falls outside the predetermined range of safe combustion values, controlling the first operator device 14 to close the inlet valve 5 in order to close the burner 1.

Advantageously, the control unit makes it possible to keep the combustion within a predetermined range of values, so that no harmful gases, such as CO, NOX, etc., are produced.

It should be noted that the ratio C (Va/Vg) between the flow rate value Va of the known comburent and the flow rate value Vg of the measured fuel is also referred to as "excess air index" and is denoted by the reference λ (lamda). It is also known that if the excess air index λ is maintained within a predetermined optimal range (essentially defined around the value recommended by the regulation for gaseous fuels "UNI EN 676" and the value recommended by the regulation for liquid fuels "UNI EN 267", and preferably equal to about 1.16), and if the coupling between the burner and the device to which it is coupled is correct and the burner 1 is correctly installed, the combustion does not produce harmful gases.

Therefore, the control unit 16 is configured to compare the ratio of the measured flow rate value Va of the comburent and the measured flow rate value Vg of the fuel with a predetermined optimum range. If the calculated ratio C (Va/Vg) is maintained within the optimum range, this means that combustion does not produce harmful gases and operates in the use range according to the relative reference regulation. If the calculated ratio C (Va/Vg) leaves the predetermined optimum range, the control unit 16 is configured to act on the first operator device 14 to close the inlet valve 5, thereby shutting off the burner 1.

It should be noted that the above-mentioned control device may form part of an assembly kit to be added to an already installed burner.

The invention also relates to a method for controlling the combustion of a burner 1 of the above-mentioned type. It should be noted that this control method is directly derived from what is described above, the entire content of which is incorporated hereinafter.

More specifically, the method includes generating an ideal flow rate value Vgr for the fuel as a function of a predetermined thermal power value Wr for the combustor 1. The step of generating the ideal flow rate value Vgr is performed as a function of a power/flow rate equation k (Wr) representing the relationship between the thermal power Wr of the burner 1 and the ideal flow rate value Vgr of the fuel.

Thereafter, the method comprises the step of measuring the flow rate Vg of the fuel fed to the burner 1 by means of the first measuring means 12.

And the method comprises the subsequent step of comparing the measured fuel flow rate value Vg with the ideal flow rate value Vgr and generating a corresponding offset value eg as a function of the difference between the measured flow rate value Vg and the ideal flow rate value Vgr.

Thereafter, the method comprises adjusting (function G (eg)) the opening of the inlet valve 5 as a function of the generated offset value eg, whereby the measured flow rate value Vg approximates the ideal fuel flow rate value Vgr. More specifically, if the ideal flow rate Vgr is greater than the measured flow rate value Vg, the opening of the inlet valve 5 is increased. If the desired flow rate value Vgr is smaller than the flow rate value Vg, the opening of the inlet valve 5 is decreased.

Also, concurrent with the above listed steps, the method comprises the steps of: an ideal flow rate value Var for comburent is generated (function h (Vg)) as a function of the measured flow rate value Vg of the fuel, according to a predetermined curve of values h (Vg) representing the relationship between the ideal comburent flow rate Va and the fuel flow rate Vg. The curve of the value h (Vg) is predetermined as a function of the type of burner 1 and defines the optimal and ideal ratio between the ideal comburent flow rate value Var and the fuel flow rate Vg.

Thereafter, the method comprises measuring the flow rate Va of the comburent supplied to the burner 1 with the second flow measuring device 13.

Furthermore, the method comprises comparing the measured flow rate value Va of the combustion air with the ideal comburent flow rate value Var and generating a corresponding offset value ε a as a function of the difference between the measured flow rate value Va and the ideal flow rate value Var.

Finally, the method comprises adjusting the flow rate of comburent flowing into the second inlet 7 as a function of the generated offset value ε a, whereby the comburent flow rate value Va measured approaches the ideal comburent quantity value Var. In other words, if the ideal flow rate Var is greater than the measured flow rate value Va, the amount of comburent supplied is increased. If the desired flow rate Var is less than the measured flow rate value Va, the amount of comburent supplied is decreased.

The invention achieves the intended objects.

More specifically, the control of the burner, carried out by the apparatus according to the invention, allows to automatically regulate the combustion by means of a double feedback check system, by means of continuous and instantaneous measurements of the comburent flow rate and of the fuel flow rate. More specifically, the control system allows to maintain the measured fuel flow rate value close to a pre-calculated comburent flow rate as a function of the required power and to maintain the comburent flow rate close to a calculated optimal flow rate value as a function of the measured fuel flow rate. In this way, the system self-regulates.

Thus, it is no longer necessary for a trained operator to set the air/gas ratio curve, especially during the start-up phase, since the combustion is maintained at an optimum level and self-regulates. In other words, the control device makes it possible to dispense with the initial and regular adjustment settings of the comburent and fuel by trained personnel.

Furthermore, the use of smoke analysis instruments by external operators is no longer required, since the fuel/comburent ratio curve has been preset in the plant in order to maintain an optimal combustion.

In addition, the present invention makes it possible to eliminate the air pressure difference switch present in many burners to measure the pressure difference between the comburent upstream of the adjustable shutter 36 and the comburent at the head. In fact, the presence of the flow rate sensor makes it possible to determine the presence or absence of comburent (and therefore to check directly whether the shutter 36 is blocked or functioning properly) without using a differential pressure switch. In this way, the invention provides greater safety for the burner, although the pressure switch is adjusted manually by the operator (who may perform an inaccurate adjustment, or the pressure switch is disturbed), the control device according to the invention does not require a manual calibration of the pressure switch, since it is based on the measurements performed by the sensors.

Furthermore, the control device self-adjusts as a function of the parameters of the comburent and/or fuel present at a specific location, thereby solving the problems related to the dependence on specific local factors that may affect the comburent (for example, air is leaner at a certain height when installed).

Moreover, the burner defines an integrated and single system with internal control, so that it is easy to install on any user equipment.

Finally, it should be noted that the burner according to the invention automatically adapts to the reference regulation for burner safety, since it is preset to comply with this regulation when leaving the plant.

It should also be noted that the present invention is relatively easy to implement and the cost of implementing the invention is relatively low.