Patent Application
20090220899
The invention relates to a method for burning gaseous fuel as described in the introduction to claim 1, and a burner as described in the introduction to claim 3, with premixing and recirculation, for the combustion of gaseous fuel.
Nitrogen oxides (denoted NOx) consist mainly of NO and NO2 and are a main component in the formation of ground-level ozone, but can also react to form nitrate particles and acid aerosols, which can affect human health by causing respiratory problems. Further, NOx contributes to formation of acid rain and global warming. Consequently, reduction of NOx formation has become a major topic in combustion research.
Generally, when using a gaseous fuel, the main pollution components are NOx, with NO as the dominating component. NOx in gas combustion is mainly formed by three mechanisms: the thermal NO mechanism, the prompt NO mechanism and the nitrous oxide (N2O) route to NOx. The different mechanisms are affected in different ways by temperature, residence time, oxygen concentration and fuel type. Thermal NO is formed by the following elementary reactions:
O+N2→NO+N (1)
N+O2→NO+O (2)
N+OH→NO+H (3)
Equation (1) is the rate limiting step and requires high temperatures to give a significant contribution to the total NOx formation because of its high activation energy. From equation (1) to (3) and the assumption that d[N]/dt≈0 it can be obtained for the NO formation that:
where [ ] denotes concentration and k1 is the rate coefficient of the reaction in equation (1). From equation (4) and the temperature dependence of k1, it can be shown that NO formation can be controlled by [O], [N2], temperature and residence time. Thermal NO formation can, therefore, be minimized by reducing peak temperatures, by reducing oxygen levels especially at peak temperatures and by reducing the time of exposure to peak temperatures.
The prompt NO mechanism involves molecular nitrogen from the combustion air reacting with the CH radical, which is an intermediate at the flame front only, forming hydrocyanic acid (HCN), which further reacts to NO:
CH+N2→HCN+N→. . . →NO
Prompt NO is favored by fuel rich conditions and its formation takes place at lower temperatures (about 1000 K) than thermal NO.
NO formation by the nitrous oxide route increases in importance under conditions such as lean mixtures, high pressure and lower combustion temperatures. This route is important in applications such as gas turbines where such conditions occur.
NOx formation can be controlled by different known techniques. Most widely used primary measures are external and internal flue gas recirculation, staged combustion and different levels of premixing. External flue gas recirculation and secondary measures such as catalytic conversion and ammonia addition can be expensive, especially on small burners, and can be difficult to install on existing equipment.
Internal flue gas recirculation is achieved when combustion products are recirculated into the unburnt fuel and combustion air mixture by a recirculation flow in the combustion chamber. The recirculated combustion products act both as an ignition source and as an inert gas that reduces the peak temperatures by dilution of the fuel and combustion air mixture. Various geometries and devices can be used to guide the flow to generate such a recirculation flow-field.
Staged combustion is applied by adding fuel and air at different stages of the combustion process. One technique is to start with a fuel rich condition, then adding more air to create an oxygen rich condition. A third stage of adding more fuel can be used before the final equivalence ratio is reached.
Premixing of fuel and air will normally result in too high combustion temperatures at stoichiometric conditions for achieving low emissions of NOx. Partial premixing, however, can, especially in combination with other techniques, give large reductions in NOx emissions.
From U.S. Pat. No. 5,049,066 (Tokyo Gas Company), a low NOx burner is described, which has a conical diverging burner head. The diverging cone is placed within an annulus where combustion air flows and is penetrated by the combustion air flowing through orifices into the cone, to be mixed with gaseous fuel supplied through a central fuel tube. The fuel is injected downstream the cone and is the mixing with combustion air occurs downstream. This is due to the turbulence generated by the air flow through and over the perforated divergent cone.
The mixing of the combustion air with the gaseous fuel inside the cone will not provide satisfactory NOx reduction.
From Norwegian patent application 20011785, a low NOx burner where fuel gas is supplied through an inner fuel tube and combustion air is supplied through a surrounding annulus is known. The outer tube restricting the annular space is terminated in a conical converging section. To provide mixing of the combustion air and the fuel gas, the fuel gas is introduced radially into a mixing zone with radial vanes providing a swirl effect.
The main object of the invention is to create a single-stage burner for combustion of gaseous fuels with low emissions of nitrogen oxides (NOx) and carbon monoxide (CO) and with high grade flame stability.
The burner should be suitable for burning natural gas (CNG, LPG), methane, butane, propane or mixtures of these and other gaseous fuels.
A further object is to provide a burner of simple design and with only minor adjustments or individual adapting to fit for a particular purpose. Otherwise expressed, the novel burner should maintain low emissions and stability over a broad range of fuel gas and varying power output and excess oxygen.
The typical about this burner is described by claim 1, while further details about the invention are given by the other claims.
The invention is providing the conditions favourable to the prevention of NOx formation with an appropriate design of the structure itself.
Primary fuel gas is injected into the combustion air and very well mixed by the turbulent flow while passing over the burner head where the flow-area cross section is decreased while flowing downstream. The reduction in cross section has the effect of accelerating the flow.
Secondary fuel is supplied creating a flame stabilization zone in front of the burner head. The said flame stabilization zone allows the main mixture of primary fuel and combustion air flowing at high velocity to be stably anchored at the burner. The high velocity of the main premixed gas mixture is unfavourable to NOx formation since the residence time in the hot zones are reduced and the equivalence ratio is such as to avoid high gas temperatures.
In the space formed inside the main annular flame and in front of the burner head, combustion products recirculate and provide further stabilisation to the overall flame, while minimizing the formation of NOx.
The most important characteristics of the burner in accordance with the invention are:
Details about the invention, including physical details of the burner, will be described more extensively in the following examples with reference to the drawings.
The invention is described in the following examples referring to the drawings, in which
The burner of the
Within the outer tube 11, an inner gaseous fuel tube 13 is arranged concentrically such that an annular space is restricted by the outer tube 11 and the inner gaseous fuel tube 13. At the outlet end of the inner gaseous fuel tube 13, a conical burner head 15 is arranged. The conical burner head 15 is diverging from the joint 16 at the end of the inner gaseous fuel tube 13, towards a downstream end where it is sealed by a cover plate 17. The burner head 15 can be integrated with the inner gaseous fuel tube 13 or joined to this tube, e.g. by welding, at the joint 16.
The burner head 15 is diverging with a half angle of 10° to 30°, preferably about 22°. Near the joint 16, the burner head 15 has a row of orifices 18 which are arranged at the circumference of the burner head 15. Primary gaseous fuel (fuel gas) is supplied through these orifices and is mixed into the surrounding combustion air flow. The primary gas is mixed into the combustion air due to turbulence generated when the air and gas mixture is accelerated over the restriction represented by the burner head 15.
At the wide end of the burner head 15, a second row of orifices 25 is arranged at the circumference. Through these orifices, secondary fuel gas is supplied into the surrounding fuel gas and combustion air mixture. The main purpose of introducing the secondary gas is to establish a pilot flame ensuring a continuous ignition of the premixed air and primary gas mixture.
Further effects of introducing secondary fuel gas at the outer end of the burner head 15 are to allow staging the total required amount of gaseous fuel. In so doing, the premixed stream of air burning in the main combustion zone is fuel lean, which is beneficial to achieve low NOx formation, as described above.
Alternatively or in addition, one orifice 26 at the centre of the cover plate 17 can be used.
The secondary injection of gaseous fuel through orifices 25 (alternatively 26) will enrich locally the flow of combustion air and primary introduced gaseous fuel, providing stabilisation of the flame in front of the burner head 15.
The burner configuration described in this example has been applied for propane as gaseous fuel. In this example, eight primary orifices 18 with a diameter of 3 mm are arranged in a circular row around the circumference of the narrow beginning 16) of the burner head 15. The outer tube 11 diameter D1 is 100 mm and the conical converging section 12 has a minimum diameter D2 of 75 mm. The inner gaseous fuel tube 13 has an outer diameter D3 of 30 mm, while the burner head 15 has a maximum diameter D4 of 70 mm and a length L1 of 50 mm. The burner head 15 is positioned in such a way that the distance L2 from the end of the conical converging section 12 to the end of the burner head 15 is 25 mm.
The burner configuration described in this example has been applied for natural gas (82.35% methane, 13.83% ethane, 1.10% butane, 1.13% nitrogen, 1.49% carbon monoxide and 0.10% heavier hydrocarbons) as gaseous fuel. The burner configuration is as described above, but some dimensions have been changed.
In this example, eight primary orifices 18 with a diameter of 4 mm are arranged in a circular row around the circumference of the narrow beginning 16 of the burner head 15. The outer tube 11 diameter D1 is 100 mm and the conical converging section 12 has a minimum diameter D2 of 75 mm. The inner gaseous fuel tube 13 has an outer diameter D3 of 30 mm, while the burner head 15 has a maximum diameter D4 of 70 mm and a length L1 of 50 mm. The burner head 15 is positioned in such a way that the distance L2 from the end of the conical converging section 12 to the end of the burner head 15 is 32 mm.
The burner configuration described in this example has been applied for propane as gaseous fuel. The burner configuration is as described above, but the dimensions have been changed.
In this example, eight primary orifices 18 with a diameter of 4.1 mm are arranged in a circular row around the circumference of the narrow beginning 16 of the burner head 15. The outer tube 11 diameter D1 is 136 mm and the conical converging section 12 has a minimum diameter D2 of 102 mm. The inner gaseous fuel tube 13 has an outer diameter D3 of 42 mm, while the burner head 15 has a maximum diameter D4 of 96 mm and a length L1 of 68 mm. The burner head 15 is positioned in such a way that the distance L2 from the end of the conical converging section 12 to the end of the burner head 15 is 34 mm.
These dimensions from examples 1 to 3 are summarized in Table 1. Emissions of NOx and CO measured from the burners described in example 1 to 3 is shown in
(1)Natural gas consisting of 82.35% methane, 13.83% ethane, 1.10% butane, 1.13% nitrogen, 1.49% carbon monoxide and 0.10% heavier hydrocarbons.
The burner can optionally be fitted with ignition probes and an ionization probe flame detector or other flame controlling equipment.
A burner as described in the first example above has been tested in a CEN tube with fuel power input in the range 80-200 kW using both methane and propane as fuel gas. Emissions of NOx has been measured in the range 10-20 parts per million while emissions of CO was measured below 10 parts per million.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2006 0170 | Jan 2006 | NO | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/NO2007/000007 | 1/10/2007 | WO | 00 | 12/18/2008 |
