EP3394512A2 - Boiler for the heating of fluids - Google Patents

Boiler for the heating of fluids

Info

Publication number
EP3394512A2
EP3394512A2 EP16826462.0A EP16826462A EP3394512A2 EP 3394512 A2 EP3394512 A2 EP 3394512A2 EP 16826462 A EP16826462 A EP 16826462A EP 3394512 A2 EP3394512 A2 EP 3394512A2
Authority
EP
European Patent Office
Prior art keywords
fluid
boiler
combustion
heat exchange
comburent
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16826462.0A
Other languages
German (de)
French (fr)
Other versions
EP3394512B1 (en
Inventor
Francesco D'ursi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Satengineering Sas Di Francesco D'ursi & C
Original Assignee
S A T Eng S A S Di Francesco Dursi & C
SAT Engineering Sas Di Francesco D'ursi & C
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by S A T Eng S A S Di Francesco Dursi & C, SAT Engineering Sas Di Francesco D'ursi & C filed Critical S A T Eng S A S Di Francesco Dursi & C
Publication of EP3394512A2 publication Critical patent/EP3394512A2/en
Application granted granted Critical
Publication of EP3394512B1 publication Critical patent/EP3394512B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • F24H1/43—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes helically or spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0026—Guiding means in combustion gas channels

Definitions

  • the present invention relates to a boiler for the heating of fluids.
  • boilers In the particular field of systems for the heating of fluids in civil and/or industrial environments, boilers are known wherein a combustible fluid and a comburent fluid are mixed to allow their combustion and to heat, therefore, a thermal carrier fluid of the water or air type.
  • boilers comprise:
  • the burner means for the combustion of the combustible fluid and of the comburent fluid to obtain a substantially aeriform and warm combustion fluid.
  • the burner means are of the premixed blown burner type, with or without metal fiber, in which the comburent air is produced by a fan and is forcibly mixed in a mixer upstream of the burner itself;
  • heat exchange means arranged inside the combustion chamber and comprising a tubular element along which the thermal carrier fluid flows which, by convection and radiation, is heated by the combustion fluid produced by the burner means.
  • the thermal carrier fluid enters the tubular element at a substantially low temperature and, after heating by means of the heat exchange with the combustion fluid, comes out of the tubular element at a higher temperature with respect to that of entry.
  • Such boilers have the main drawback of using only a part of the sensitive heat of the combustion fluid.
  • Boilers are also known which, thanks to their high performance and operating efficiency are called “high-yield” and which allow recovering a large part of the latent heat of the combustion fluid.
  • Such boilers in fact, allow cooling the combustion fluid, which yields heat to the thermal carrier fluid to be heated, until a state transition from gaseous to saturated liquid is achieved.
  • the latent heat of the combustion fluid, during state transition, is recovered and supplied to the thermal carrier fluid to be heated.
  • the condensing boilers of known type have burner means of the premixed type thanks to which, upon variation of the power of the burner means themselves, it is possible to maintain low emissions of CO (carbon monoxide) and NOx (nitrogen monoxide and dioxide).
  • such condensing boilers comprising burner means of the premixed type have a main drawback tied to the difficulty of obtaining the condensation of the water vapor present in the combustion fluid and recovering the latent heat of the combustion fluid itself.
  • This solution is adopted to facilitate the combustion of the first combustible fluid and the second comburent fluid higher on the surface of the burner head, and make the radiating-pattern mesh operate at low thermal loads.
  • the main aim of the present invention is to provide a boiler for the heating of fluids which has a broad modulation range and low and stable emissions at all operating powers.
  • One object of the present invention is to provide a boiler for the heating of fluids comprising burner means which allow avoiding the formation of potentially dangerous explosive mixtures during the combustion.
  • a further object of the present invention is to provide a boiler for the heating of fluids comprising burner means which allow generating a flame of great power which remains stably lit in small volumes of air.
  • Another object of the present invention is to provide a boiler for the heating of fluids which allows reducing energy consumption, and maximizing production capacity, thus obtaining a better environmental impact than boilers of known type.
  • Another object of the present invention is to provide a boiler for the heating of fluids which allows to overcome the mentioned drawbacks of the prior art within the ambit of a simple, rational, easy, effective to use and affordable solution.
  • FIG. 1 is a schematic view of the boiler according to the invention.
  • Figure 2 is a side view of a detail of the burner of the boiler according to the invention.
  • Figure 3 is a sectional view of a detail of the burner of the boiler according to the invention.
  • Figure 4 is a perspective view of a detail of the burner of the boiler according to the invention
  • Figure 5 is a sectional view of a detail of the burner of the boiler according to the invention.
  • reference numeral 1 is a boiler for the heating of fluids.
  • the boiler 1 comprises:
  • the burner means 31 are associated with the combustion chamber 2.
  • the first combustible fluid Fl is, e.g., methane or other gaseous fuel
  • the second comburent fluid F2 is, e.g., air;
  • the fourth thermal carrier fluid F4 is of the water type.
  • the burner means 31 comprise at least one burner 9 of the non-premixed type.
  • non-premixed is meant the particular category of burners in which the first combustible fluid Fl is taken from a relative conduit without mixing it with the second comburent fluid F2, the union between the first combustible fluid Fl and the second comburent fluid F2 taking place at the time of the formation of the flame.
  • the burner means 31 also comprise:
  • a fan element 14 adapted to move the second comburent fluid F2;
  • first duct 12 connected to the fan element 14, and in which the second comburent fluid F2 circulates, the first duct 12 comprising a first pressure transducer 17 for the second comburent fluid F2;
  • the ignition device 10 is of the type of an electrode
  • a second duct 11 of the type of a feeding pipe, isolated from the first duct 12, in which the first combustible fluid Fl circulates, the second duct 11 comprising a second pressure transducer 16 for the first combustible fluid Fl;
  • adjusting means 15 of the first combustible fluid Fl comprising blocking and safety solenoid valves which adjust the delivery of the first combustible fluid Fl.
  • the burner means 31 comprise a ventilation pipe 13 adapted to suck the second comburent fluid F2 and to the channeling thereof at the fan element 14.
  • the ventilation pipe 13 is adapted to stabilize the turbulence of the second comburent fluid F2 at input of the fan element 14, thus allowing reducing the noise due to the combustion between the first combustible fluid Fl and the second comburent fluid F2.
  • the burner 9 comprises:
  • a first injector body 30 substantially hollow, and preferably made of a metal material, comprising a passage channel 28 connected to the second duct 11 of the first combustible fluid Fl, the first injector body 30 comprising a plurality of passage holes 19 connected to the passage channel 28 adapted to deliver the first combustible fluid Fl.
  • the passage holes 19 are radially arranged along the lateral surface of the first injector body 30 and have an axis preferably perpendicular to the axis of the first body itself; a second body 24 substantially hollow associated on top of the first injector body 30 and adapted to define a mixing area 23 wherein the first part of combustion takes place between the first combustible fluid Fl and the second comburent fluid F2.
  • the second body 24 is substantially made of a metal material; and
  • the first duct 12 is associated with the second body 24 to define the extension of the second body itself for the channeling of the second comburent fluid F2 at the recirculation element 21.
  • the recirculation element 21 is of the type of a "s wirier" made of a metal material and has a substantially cylindrical conformation along an extension axis.
  • the recirculation element 21 comprises a plurality of grooves 22 preferably of square, rectangular or circular shape which extend substantially inclined with respect to the extension axis, inside which the second comburent fluid F2 flows.
  • the angle of inclination of the grooves 22 defines the particular swirling/spiral motion of the flame generated by the combustion between the first combustible fluid Fl and the second comburent fluid F2.
  • the particular swirling/spiral motion of flame promotes greater heat distribution to the heat exchange means 32 than the distribution obtained with the flame generated by the burners of known type.
  • This flame while having small dimensions, allows obtaining a huge quantity of combustion fluid F3 and therefore high heating efficiency.
  • the flame succeeds therefore in supplying heat to the heat exchange means 32 while not coming into contact directly with the heat exchange means themselves, therefore avoiding the related corrosion phenomena.
  • the first injector body 30 has a substantially cylindrical and elongated conformation and comprises an end portion 20 arranged in the proximity of the mixing area 23, at which the combustion takes place between the first combustible fluid Fl and the second comburent fluid F2, the passage holes 19 being arranged in the proximity of the end portion 20.
  • the end portion 20 has a substantially frusto-conical conformation such as to promote adherence to the flame at the end portion itself and avoid the phenomenon of "flame detachment".
  • the first injector body 30 comprises a first abutment surface 29 adapted to define a substantially airtight coupling with the recirculation element 21 which, in more detail, is arranged substantially in abutment with the first injector body 30 at the abutment surface itself.
  • the recirculation element 21 comprises at least one through hole 27 adapted to contain the first injector body 30, the through hole 27 being substantially coaxial to the first injector body 30 and to the extension axis.
  • the second body 24 comprises a flanged element 25, arranged on the outer surface of the second body itself, which allows the coupling of the burner 9 to the combustion chamber 2 and to the heat exchange means 32.
  • combustion chamber 2 comprises coupling means arranged at the connection between the burner 9 and the heat exchange means 32.
  • the second body 24 comprises an abutment edge 26, arranged on the inner surface of the second body itself, adapted to define a coupling between the recirculation element 21 arranged in abutment with the second body itself.
  • the boiler 1 comprises a command unit, for the boiler operation, operatively connected to the first pressure transducer 17, to the second pressure transducer 16, to the adjusting means 15 and to the fan element 14.
  • the command unit is of the type of a controller with microprocessor which receives the electrical signals from the first pressure transducer 17 and from the second pressure transducer 16.
  • This controller processes the electrical signals by means of a suitable PID ("Proportional - Integral - Derivative") algorithm and calculates the power of the burner 9.
  • PID Proportional - Integral - Derivative
  • the command unit operates on the power of the burner 9 by means of the adjusting means 15 by correcting the flow rate of the first combustible fluid Fl.
  • command unit can be operatively connected to a control device, of the type of an inverter, adapted to correct the flow rate of the second comburent fluid F2.
  • the heat exchange means 32 comprise a tubular element 32 wound helically around a central axis.
  • the fourth thermal carrier fluid F4 circulates inside the tubular element itself and the third combustion fluid F3 externally laps the tubular element 32.
  • the central axis has a substantially horizontal extension.
  • the helix winding of the tubular element 32 around the central axis defines a hollow inner area, which extends radially around the central axis between the central axis itself and the tubular element 32.
  • the particular helix conformation of the tubular element 32 defines a plurality of coils which are slightly spaced apart and, more particularly, between each coil and the other an empty space is defined.
  • the tubular element 32 comprises:
  • a second section 34 having a second opening 8 adapted to the outflow of the fourth thermal carrier fluid F4 from the tubular element itself.
  • the fourth thermal carrier fluid F4 entering the first opening 7 is substantially colder and, going upstream along the tubular element 32, is heated by convection through the third combustion fluid F3 that laps the tubular element 32.
  • the fourth thermal carrier fluid F4 exiting the second opening 8 has therefore a higher temperature than the related temperature at input of the first opening 7, and is usefully employed by heating systems.
  • the combustion chamber 2 comprises at least a first baffle 6a arranged substantially transverse to the central axis and adapted to the separation of a first heat exchange area 3 from a second heat exchange area 4.
  • the first section 33 is arranged at the second heat exchange area 4 and the second section 34 is arranged at the first heat exchange area 3.
  • the first baffle 6a is adapted to the deviation of the path of the third combustion fluid F3 with respect to the central axis in the passage from the first heat exchange area 3 to the second heat exchange area 4.
  • the third combustion fluid F3 flows outside the empty inner area.
  • the third combustion fluid F3 passing between the empty spaces interposed between one coil and the other of the tubular element 32, and exiting the empty inner area, has a bigger path within the combustion chamber 2 than that it would have without the first baffle 6a.
  • the path of the third combustion fluid F3 is bigger and slower, thus promoting greater heat exchange between the third combustion fluid itself and the fourth thermal carrier fluid F4.
  • the combustion chamber 2 comprises a second baffle 6b, having a substantially cylindrical conformation, interposed between the tubular element 32 and the inner wall of the combustion chamber 2 outside of the empty inner area.
  • the second baffle 6b is adapted to bring the third combustion fluid F3 within the empty inner area to the second heat exchange area 4.
  • the combustion chamber 2 also comprises:
  • first outlet conduit 18 adapted to the expulsion of the third combustion fluid F3 from the boiler 1.
  • first outlet conduit 18 is adapted to the expulsion from the boiler 1 of the third combustion fluid F3 contained in the empty inner area of the second heat exchange area 4; and a second outlet conduit 5, adapted to the expulsion of a fifth condensation fluid F5 from the boiler 1.
  • the second outlet conduit 5 is connected to the second heat exchange area 4.
  • the fifth condensation fluid F5 is substantially a mixture of water, carbonic acid, nitric acid and possibly sulfuric acid.
  • the third combustion fluid F3 exiting the mixing area 23 is substantially warm and is channeled inside the combustion chamber 2, and more precisely at the empty inner area, where it laps the coils of the tubular element 32.
  • the fourth thermal carrier fluid F4 entering the first section 33 of the tubular element 32 through the first opening 7, is substantially colder and has a much lower temperature than the temperature of the third combustion fluid F3.
  • the heat exchange takes place, at a higher temperature, between the fourth thermal carrier fluid F4 and the third combustion fluid F3.
  • This exchange implies that the latent heat of the third combustion fluid F3 is recovered by the fourth thermal carrier fluid F4 and, within the second heat exchange area 4, the water vapor contained in the third combustion fluid F3 undergoes a transformation of state from gaseous to liquid which implies the formation of the fifth condensation fluid F5.
  • the fifth condensation fluid F5 accumulated in the second heat exchange area 4 is ejected from the boiler 1 through the second outlet conduit 5.
  • the difference in temperature between the third combustion fluid F3 and the fourth thermal carrier fluid F4 decreases gradually as the fourth thermal carrier fluid itself flows along the tubular element 32 and approaches the burner 9.
  • the fourth thermal carrier fluid F4 is substantially warm and is channeled in the second section 34 from which it exits through the second opening 8 and is used by the heating systems.
  • the boiler thus made has stable emissions at all operating powers and allows avoiding the formation of potentially dangerous explosive mixtures during combustion.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Abstract

The boiler (1) for the heating of fluids comprises: a combustion chamber (2); - burner means (31) of a first combustible fluid (Fl), substantially aeriform, and a second comburent fluid (F2), substantially aeriform, to obtain a third combustion fluid (F3) substantially aeriform, the burner means (31) being associated with the combustion chamber (2); heat exchange means (32) arranged inside the combustion chamber (2), the third combustion fluid (F3) lapping the heat exchange means (32) for the heating of a fourth thermal carrier fluid (F4); wherein the burner means (31) comprise a burner (9) of the non-premixed type.

Description

BOILER FOR THE HEATING OF FLUIDS
Technical Field
The present invention relates to a boiler for the heating of fluids.
Background Art
In the particular field of systems for the heating of fluids in civil and/or industrial environments, boilers are known wherein a combustible fluid and a comburent fluid are mixed to allow their combustion and to heat, therefore, a thermal carrier fluid of the water or air type.
Generally, boilers comprise:
- a combustion chamber;
burner means for the combustion of the combustible fluid and of the comburent fluid to obtain a substantially aeriform and warm combustion fluid. Generally, the burner means are of the premixed blown burner type, with or without metal fiber, in which the comburent air is produced by a fan and is forcibly mixed in a mixer upstream of the burner itself; and
heat exchange means arranged inside the combustion chamber and comprising a tubular element along which the thermal carrier fluid flows which, by convection and radiation, is heated by the combustion fluid produced by the burner means.
The thermal carrier fluid enters the tubular element at a substantially low temperature and, after heating by means of the heat exchange with the combustion fluid, comes out of the tubular element at a higher temperature with respect to that of entry.
Such boilers have the main drawback of using only a part of the sensitive heat of the combustion fluid.
Boilers are also known which, thanks to their high performance and operating efficiency are called "high-yield" and which allow recovering a large part of the latent heat of the combustion fluid.
Such boilers, in fact, allow cooling the combustion fluid, which yields heat to the thermal carrier fluid to be heated, until a state transition from gaseous to saturated liquid is achieved.
The latent heat of the combustion fluid, during state transition, is recovered and supplied to the thermal carrier fluid to be heated.
The condensing boilers of known type have burner means of the premixed type thanks to which, upon variation of the power of the burner means themselves, it is possible to maintain low emissions of CO (carbon monoxide) and NOx (nitrogen monoxide and dioxide).
These boilers of known type do have some drawbacks.
In particular, such condensing boilers comprising burner means of the premixed type have a main drawback tied to the difficulty of obtaining the condensation of the water vapor present in the combustion fluid and recovering the latent heat of the combustion fluid itself.
Another drawback of condensing boilers with burner means of the premixed type is represented by the overheating of the burner body with low thermal power inasmuch as the comburent air flow rate is not sufficient to cool the burner body itself.
Another drawback of the boilers of known type is tied to the poor modulation field and stability of the flame and excessive emissions of CO (carbon monoxide) and NOx (nitrogen monoxide and dioxide) as a result of combustion, due to the premixed combustion means.
Yet another drawback of condensing boilers comprising burner means of the premixed type is tied to the phenomenon of "backfire" and "flame detachment" especially when the pressures, flow rates and type of combustible fluid vary. Regardless of the type of burner, the phenomena of "backfire" and "flame detachment" occur when the balance changes between the speed of outflow of the mixture made up of the first combustible fluid and of the second comburent fluid and that of flame propagation.
Not the least inconvenience is tied to the high manufacturing costs of the premixed burners, especially when the solution is adopted of covering the burner head with metal fiber.
This solution is adopted to facilitate the combustion of the first combustible fluid and the second comburent fluid higher on the surface of the burner head, and make the radiating-pattern mesh operate at low thermal loads.
Description of the Invention The main aim of the present invention is to provide a boiler for the heating of fluids which has a broad modulation range and low and stable emissions at all operating powers.
One object of the present invention is to provide a boiler for the heating of fluids comprising burner means which allow avoiding the formation of potentially dangerous explosive mixtures during the combustion.
By so doing, the problems tied to "backfire" are avoided.
A further object of the present invention is to provide a boiler for the heating of fluids comprising burner means which allow generating a flame of great power which remains stably lit in small volumes of air.
Another object of the present invention is to provide a boiler for the heating of fluids which allows reducing energy consumption, and maximizing production capacity, thus obtaining a better environmental impact than boilers of known type.
Another object of the present invention is to provide a boiler for the heating of fluids which allows to overcome the mentioned drawbacks of the prior art within the ambit of a simple, rational, easy, effective to use and affordable solution.
The above mentioned objects are achieved by the present boiler for the heating of fluids having the characteristics of claim 1.
Brief Description of the Drawings
Other characteristics and advantages of the present invention will become better evident from the description of a preferred, but not exclusive, embodiment of a boiler for the heating of fluids, illustrated by way of an indicative, but non- limiting, example in the accompanying drawings, wherein:
Figure 1 is a schematic view of the boiler according to the invention;
Figure 2 is a side view of a detail of the burner of the boiler according to the invention;
Figure 3 is a sectional view of a detail of the burner of the boiler according to the invention;
Figure 4 is a perspective view of a detail of the burner of the boiler according to the invention; Figure 5 is a sectional view of a detail of the burner of the boiler according to the invention.
Embodiments of the Invention
With particular reference to such figures, globally indicated with reference numeral 1 is a boiler for the heating of fluids.
The boiler 1 comprises:
a combustion chamber 2;
burner means 31 of a first combustible fluid Fl and substantially aeriform and at least a second comburent fluid F2 and substantially aeriform to obtain a third combustion fluid F3 substantially aeriform. In the particular embodiment shown in Figure 1, the burner means 31 are associated with the combustion chamber 2. The first combustible fluid Fl is, e.g., methane or other gaseous fuel, while the second comburent fluid F2 is, e.g., air;
heat exchange means 32 arranged inside the combustion chamber 2, the third combustion fluid F3 lapping the heat exchange means 32 for the heating of a fourth thermal carrier fluid F4. The fourth thermal carrier fluid F4 is of the water type.
According to the invention, the burner means 31 comprise at least one burner 9 of the non-premixed type.
In the present context, by the term "non-premixed" is meant the particular category of burners in which the first combustible fluid Fl is taken from a relative conduit without mixing it with the second comburent fluid F2, the union between the first combustible fluid Fl and the second comburent fluid F2 taking place at the time of the formation of the flame.
The burner means 31 also comprise:
a fan element 14 adapted to move the second comburent fluid F2;
a first duct 12, connected to the fan element 14, and in which the second comburent fluid F2 circulates, the first duct 12 comprising a first pressure transducer 17 for the second comburent fluid F2;
- a flame ignition device 10, revealing the presence of the flame itself, due to the combustion between the first combustible fluid Fl and the second comburent fluid F2. Preferably, the ignition device 10 is of the type of an electrode;
a second duct 11, of the type of a feeding pipe, isolated from the first duct 12, in which the first combustible fluid Fl circulates, the second duct 11 comprising a second pressure transducer 16 for the first combustible fluid Fl;
adjusting means 15 of the first combustible fluid Fl comprising blocking and safety solenoid valves which adjust the delivery of the first combustible fluid Fl.
Preferably, the burner means 31 comprise a ventilation pipe 13 adapted to suck the second comburent fluid F2 and to the channeling thereof at the fan element 14.
In addition, the ventilation pipe 13 is adapted to stabilize the turbulence of the second comburent fluid F2 at input of the fan element 14, thus allowing reducing the noise due to the combustion between the first combustible fluid Fl and the second comburent fluid F2.
Within the ambit of the present context, the burner 9 comprises:
a first injector body 30 substantially hollow, and preferably made of a metal material, comprising a passage channel 28 connected to the second duct 11 of the first combustible fluid Fl, the first injector body 30 comprising a plurality of passage holes 19 connected to the passage channel 28 adapted to deliver the first combustible fluid Fl. In more detail, the passage holes 19 are radially arranged along the lateral surface of the first injector body 30 and have an axis preferably perpendicular to the axis of the first body itself; a second body 24 substantially hollow associated on top of the first injector body 30 and adapted to define a mixing area 23 wherein the first part of combustion takes place between the first combustible fluid Fl and the second comburent fluid F2. Preferably, the second body 24 is substantially made of a metal material; and
a recirculation element 21 of the second comburent fluid F2 arranged in the proximity of the passage holes 19.
In the preferred embodiment, the first duct 12 is associated with the second body 24 to define the extension of the second body itself for the channeling of the second comburent fluid F2 at the recirculation element 21.
Alternative embodiments cannot however be ruled out for the connection between the burner 9 and the first duct 12 provided that the mixing between the first combustible fluid Fl and the second comburent fluid F2 does not occur prior to the ignition of the flame.
Preferably, the recirculation element 21 is of the type of a "s wirier" made of a metal material and has a substantially cylindrical conformation along an extension axis.
The recirculation element 21 comprises a plurality of grooves 22 preferably of square, rectangular or circular shape which extend substantially inclined with respect to the extension axis, inside which the second comburent fluid F2 flows.
Advantageously, the angle of inclination of the grooves 22 defines the particular swirling/spiral motion of the flame generated by the combustion between the first combustible fluid Fl and the second comburent fluid F2.
The particular swirling/spiral motion of flame promotes greater heat distribution to the heat exchange means 32 than the distribution obtained with the flame generated by the burners of known type.
This flame, while having small dimensions, allows obtaining a huge quantity of combustion fluid F3 and therefore high heating efficiency.
Advantageously, the flame succeeds therefore in supplying heat to the heat exchange means 32 while not coming into contact directly with the heat exchange means themselves, therefore avoiding the related corrosion phenomena.
The first injector body 30 has a substantially cylindrical and elongated conformation and comprises an end portion 20 arranged in the proximity of the mixing area 23, at which the combustion takes place between the first combustible fluid Fl and the second comburent fluid F2, the passage holes 19 being arranged in the proximity of the end portion 20.
Conveniently, the end portion 20 has a substantially frusto-conical conformation such as to promote adherence to the flame at the end portion itself and avoid the phenomenon of "flame detachment".
The first injector body 30 comprises a first abutment surface 29 adapted to define a substantially airtight coupling with the recirculation element 21 which, in more detail, is arranged substantially in abutment with the first injector body 30 at the abutment surface itself.
The recirculation element 21 comprises at least one through hole 27 adapted to contain the first injector body 30, the through hole 27 being substantially coaxial to the first injector body 30 and to the extension axis.
In the preferred embodiment, the second body 24 comprises a flanged element 25, arranged on the outer surface of the second body itself, which allows the coupling of the burner 9 to the combustion chamber 2 and to the heat exchange means 32.
An alternative embodiment cannot however be ruled out in which the combustion chamber 2 comprises coupling means arranged at the connection between the burner 9 and the heat exchange means 32.
In addition, the second body 24 comprises an abutment edge 26, arranged on the inner surface of the second body itself, adapted to define a coupling between the recirculation element 21 arranged in abutment with the second body itself.
It cannot also be ruled out that the boiler 1 comprises a command unit, for the boiler operation, operatively connected to the first pressure transducer 17, to the second pressure transducer 16, to the adjusting means 15 and to the fan element 14.
Preferably, the command unit is of the type of a controller with microprocessor which receives the electrical signals from the first pressure transducer 17 and from the second pressure transducer 16.
This controller processes the electrical signals by means of a suitable PID ("Proportional - Integral - Derivative") algorithm and calculates the power of the burner 9.
Advantageously, the command unit operates on the power of the burner 9 by means of the adjusting means 15 by correcting the flow rate of the first combustible fluid Fl.
Furthermore, the command unit can be operatively connected to a control device, of the type of an inverter, adapted to correct the flow rate of the second comburent fluid F2. The heat exchange means 32 comprise a tubular element 32 wound helically around a central axis.
In particular, the fourth thermal carrier fluid F4 circulates inside the tubular element itself and the third combustion fluid F3 externally laps the tubular element 32.
In more detail, the central axis has a substantially horizontal extension.
Alternative embodiments cannot however be ruled out in which the central axis has a substantially vertical extension and, therefore, the boiler 1 is positioned according to different orientations as shown in Figure 1.
In particular, the helix winding of the tubular element 32 around the central axis defines a hollow inner area, which extends radially around the central axis between the central axis itself and the tubular element 32.
Moreover, the particular helix conformation of the tubular element 32 defines a plurality of coils which are slightly spaced apart and, more particularly, between each coil and the other an empty space is defined.
The tubular element 32 comprises:
a first section 33, having a first opening 7 adapted to the input of the fourth thermal carrier fluid F4 inside the tubular element itself; and
a second section 34, having a second opening 8 adapted to the outflow of the fourth thermal carrier fluid F4 from the tubular element itself.
In more detail, the fourth thermal carrier fluid F4 entering the first opening 7 is substantially colder and, going upstream along the tubular element 32, is heated by convection through the third combustion fluid F3 that laps the tubular element 32.
The fourth thermal carrier fluid F4 exiting the second opening 8 has therefore a higher temperature than the related temperature at input of the first opening 7, and is usefully employed by heating systems.
The combustion chamber 2 comprises at least a first baffle 6a arranged substantially transverse to the central axis and adapted to the separation of a first heat exchange area 3 from a second heat exchange area 4.
In the preferred embodiment shown in Figure 1, the first section 33 is arranged at the second heat exchange area 4 and the second section 34 is arranged at the first heat exchange area 3.
The first baffle 6a is adapted to the deviation of the path of the third combustion fluid F3 with respect to the central axis in the passage from the first heat exchange area 3 to the second heat exchange area 4.
In more detail, the third combustion fluid F3 flows outside the empty inner area. Conveniently, the third combustion fluid F3 passing between the empty spaces interposed between one coil and the other of the tubular element 32, and exiting the empty inner area, has a bigger path within the combustion chamber 2 than that it would have without the first baffle 6a.
This way, advantageously, the path of the third combustion fluid F3 is bigger and slower, thus promoting greater heat exchange between the third combustion fluid itself and the fourth thermal carrier fluid F4.
Preferably, the combustion chamber 2 comprises a second baffle 6b, having a substantially cylindrical conformation, interposed between the tubular element 32 and the inner wall of the combustion chamber 2 outside of the empty inner area.
Usefully, the second baffle 6b is adapted to bring the third combustion fluid F3 within the empty inner area to the second heat exchange area 4.
The combustion chamber 2 also comprises:
- a first outlet conduit 18, adapted to the expulsion of the third combustion fluid F3 from the boiler 1. In more detail, the first outlet conduit 18 is adapted to the expulsion from the boiler 1 of the third combustion fluid F3 contained in the empty inner area of the second heat exchange area 4; and a second outlet conduit 5, adapted to the expulsion of a fifth condensation fluid F5 from the boiler 1.
In the preferred embodiment shown in Figure 1, the second outlet conduit 5 is connected to the second heat exchange area 4.
The fifth condensation fluid F5 is substantially a mixture of water, carbonic acid, nitric acid and possibly sulfuric acid.
The operation of the present invention is described below.
The first combustible fluid Fl and the second comburent fluid F2 conveyed through the second duct 11 and the first duct 12 respectively, come within the mixing area 23 and by means of the activation of the ignition device 10 the combustion takes place, and then the formation of the flame, by obtaining the third combustion fluid F3.
The third combustion fluid F3 exiting the mixing area 23 is substantially warm and is channeled inside the combustion chamber 2, and more precisely at the empty inner area, where it laps the coils of the tubular element 32.
The fourth thermal carrier fluid F4, entering the first section 33 of the tubular element 32 through the first opening 7, is substantially colder and has a much lower temperature than the temperature of the third combustion fluid F3.
At the first heat exchange area 3 the heat exchange takes place, at a higher temperature, between the fourth thermal carrier fluid F4 and the third combustion fluid F3.
The third combustion fluid F3, lapping the coils of the tubular element 32 in the first heat exchange area 3, transfers heat to the fourth thermal carrier fluid F4 circulating in the tubular element itself.
This exchange implies that the latent heat of the third combustion fluid F3 is recovered by the fourth thermal carrier fluid F4 and, within the second heat exchange area 4, the water vapor contained in the third combustion fluid F3 undergoes a transformation of state from gaseous to liquid which implies the formation of the fifth condensation fluid F5.
The fifth condensation fluid F5 accumulated in the second heat exchange area 4 is ejected from the boiler 1 through the second outlet conduit 5.
The difference in temperature between the third combustion fluid F3 and the fourth thermal carrier fluid F4 decreases gradually as the fourth thermal carrier fluid itself flows along the tubular element 32 and approaches the burner 9.
In the proximity of the burner 9, in fact, the fourth thermal carrier fluid F4 is substantially warm and is channeled in the second section 34 from which it exits through the second opening 8 and is used by the heating systems.
The third combustion fluid F3, after having transferred its heat to the fourth thermal carrier fluid F4 in the first heat exchange area 3, is ejected from the second heat exchange area 4 through the first outlet conduit 18 that channels it outside of the boiler 1. It has in practice been ascertained that the described invention achieves the intended objects and in particular the fact is underlined that the boiler thus made allows reducing the environmental impact and optimizing the energy efficiency by maximizing the latent heat recovery of the third combustion fluid for the heating of the fourth thermal carrier fluid.
The boiler thus made has stable emissions at all operating powers and allows avoiding the formation of potentially dangerous explosive mixtures during combustion.

Claims

1) Boiler (1) for the heating of fluids, comprising:
at least one combustion chamber (2);
burner means (31) of at least one first combustible fluid (Fl) and substantially aeriform and at least one second comburent fluid (F2) and substantially aeriform to obtain at least one third combustion fluid (F3) substantially aeriform, said burner means (31) being associated with said combustion chamber (2);
heat exchange means (32) arranged inside said combustion chamber (2), said third combustion fluid (F3) lapping said heat exchange means (32) for the heating of a fourth thermal carrier fluid (F4);
characterized in that said burner means (31) comprise at least one burner (9) of the non-premixed type.
2) Boiler (1) according to claim 1, characterized in that said burner means (31) comprise:
at least one fan element (14) suitable for the movement of said second comburent fluid (F2);
at least one first duct (12), connected to said fan element (14), in which said second comburent fluid (F2) circulates;
- at least one flame ignition device (10), and revealing the presence of the flame itself, due to the combustion between said first combustible fluid (Fl) and said second comburent fluid (F2);
at least one second duct (11) in which said first combustible fluid (Fl) circulates;
- adjusting means (15) of said first combustible fluid (Fl).
3) Boiler (1) according to one or more of the preceding claims, characterized in that said burner (9) comprises:
at least one first injector body (30) substantially hollow comprising a passage channel (28) connected to said second duct (11), said first injector body (30) comprising a plurality of passage holes (19) connected to said passage channel (28) and suitable for the dispensing of said first combustible fluid (Fl); at least one second body (24) substantially hollow associated on top of said first injector body (30) and able to define a mixing area (23) of said first combustible fluid (Fl) and of said second comburent fluid (F2) to obtain said third combustion fluid (F3); and
- at least one recirculation element (21) of said second comburent fluid (F2) arranged in the proximity of said passage holes (19), said recirculation element (21) comprising a plurality of grooves (22) inside which said second comburent fluid (F2) flows.
4) Boiler (1) according to one or more of the preceding claims, characterized in that said first injector body (30) has a substantially cylindrical and elongated conformation and comprises an end portion (20), arranged in the proximity of said mixing area (23), at which the combustion takes place of said first combustible fluid (Fl) and said second comburent fluid (F2) and the obtainment of said third combustion fluid (F3), said passage holes (19) being arranged in the proximity of said end portion (20).
5) Boiler (1) according to one or more of the preceding claims, characterized in that said first injector body (30) comprises at least one abutment surface (29) able to define a substantially airtight coupling with said recirculation element (21), said recirculation element (21) being arranged substantially in abutment with said first injector body (30) at said abutment surface (29).
6) Boiler (1) according to one or more of the preceding claims, characterized in that said recirculation element (21) has a substantially cylindrical conformation and comprises at least one through hole (27) able to contain said first injector body (30), said through hole (27) being substantially coaxial to said first injector body (30).
7) Boiler (1) according to one or more of the preceding claims, characterized in that:
said first duct (12) comprises at least one first pressure transducer (17) of said second comburent fluid (F2); and
- said second duct (11) comprises at least one second pressure transducer (16) of said first combustible fluid (Fl).
8) Boiler (1) according to one or more of the preceding claims, characterized in that it comprises at least one command unit operatively connected to at least one of said first pressure transducer, second pressure transducer, adjusting means and fan element (17, 16, 15, 14).
9) Boiler (1) according to one or more of the preceding claims, characterized in that said heat exchange means (32) comprise at least one tubular element (32) wound helically around a central axis, said fourth thermal carrier fluid (F4) circulating inside said tubular element (32) and said third combustion fluid (F3) lapping externally said tubular element (32).
10) Boiler (1) according to one or more of the preceding claims, characterized in that said tubular element (32) comprises:
at least one first section (33) having at least one first opening (7) for the input of said fourth thermal carrier fluid (F4) inside said tubular element (32); and
at least one second section (34) having at least one second opening (8) for the outflow of said fourth thermal carrier fluid (F4) from said tubular element (32).
11) Boiler (1) according to one or more of the preceding claims, characterized in that said combustion chamber (2) comprises at least one first baffle (6a) suitable for the separation of a first heat exchange area (3) from a second heat exchange area (4), said first baffle (6a) being arranged substantially transverse to said central axis and suitable for the deviation of the path of said third combustion fluid (F3) with respect to said central axis in the passage from said first heat exchange area (3) to said second heat exchange area (4), said first section (33) being arranged at said second heat exchange area (4) and said second section (34) being arranged at said first heat exchange area (3).
12) Boiler (1) according to one or more of the preceding claims, characterized in that said combustion chamber (2) comprises:
at least one first outlet conduit (18) for the expulsion of said third combustion fluid (F3) from said boiler (1); and
- at least one second outlet conduit (5) for the expulsion of a fifth condensation fluid (F5) from said boiler (1).
EP16826462.0A 2015-12-21 2016-12-21 Boiler for the heating of fluids Active EP3394512B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUB2015A009531A ITUB20159531A1 (en) 2015-12-21 2015-12-21 BOILER FOR FLUID HEATING
PCT/IB2016/057857 WO2017109714A2 (en) 2015-12-21 2016-12-21 Boiler for the heating of fluids

Publications (2)

Publication Number Publication Date
EP3394512A2 true EP3394512A2 (en) 2018-10-31
EP3394512B1 EP3394512B1 (en) 2020-02-12

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EP (1) EP3394512B1 (en)
IT (1) ITUB20159531A1 (en)
WO (1) WO2017109714A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109827174A (en) * 2019-02-19 2019-05-31 付福来 A kind of environment-friendly highly efficient gas heater combustion chamber
CN110553390A (en) * 2019-07-23 2019-12-10 曌能科技(澳门)有限公司 Ultralow nitrogen oxide combustion apparatus

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3182711A (en) * 1962-03-26 1965-05-11 Midland Ross Corp Nozzle mixing type gas burner
ATE195367T1 (en) * 1996-04-20 2000-08-15 Al Halbouni Ahmad FIRE ROOM WITH A BURNER DEVICE AND METHOD FOR OPERATING A FIRE ROOM
IT1399383B1 (en) * 2010-03-29 2013-04-16 Ancora Spa BURNER WITH HIGH FLAME STABILITY, PARTICULARLY FOR THE THERMAL TREATMENT OF CERAMIC MANUFACTURES.

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WO2017109714A3 (en) 2017-08-03
EP3394512B1 (en) 2020-02-12
WO2017109714A2 (en) 2017-06-29
ITUB20159531A1 (en) 2017-06-21

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