Patent Grant
6984122
This invention relates to combustion control directed to maintaining fuel efficiency and minimal emissions of air pollutants, especially nitrogen oxides (NOx). More particularly, the invention provides a combustion control system to maintain a selected fuel-air ratio that is improved in that density changes of a reactant, usually air, caused by temperature variations, are compensated for.
Two types of combustion control systems are commonly used (both illustrated in
A principal object of this invention is to provide an improved combustion control system that in response to temperature changes of the reactants, usually air alone, automatically varies the flow of fuel or air to maintain a substantially constant target fuel-air ratio.
Another object is to minimize the use of mechanical linkages in the control system.
These and other features and advantages of the invention will be apparent from the description which follows.
Basically, the invention incorporates in current combustion control systems means for measuring temperature variations of the air stream and for automatically causing the variations to adjust the flow of fuel or air to maintain a target fuel air ratio. In one embodiment of the invention, known combustion control systems are improved by the placement of a flow regulator in the fuel or air supply line in series with the usual flow regulator of that line. This additional flow regulator is remotely operated in combination with, and in relation to, temperature responsive means that monitor the air stream temperature.
The additional flow regulator that is remotely operated can be a valve or damper that is operated electrically, pneumatically or hydraulically. Such choices of the additional flow regulator are intended in the term, “remote control-flow regulator”, used hereinafter.
To facilitate further description and understanding of the invention, reference will be made to the accompanying drawings of which:
The invention as applied to
In
To make the “two-point parallel” positioning system more accurate by adjusting for air density variations caused by air temperature changes, the invention provides the insertion of a remote control-flow regulator, specifically, electrically operated valve 21 in fuel supply line 4 downstream (optionally can be upstream) of valve 5A as well as the addition of temperature sensor 22 in air duct 1 near burner 3. Sensor 22 passes temperature variation signals through line 23 to converter 24 that electrically controls the operation of valve 21. Thus, when the air temperature drops, valve 21 will adjust for greater flow of fuel to compensate for the flow of denser air and will adjust conversely when air temperature rises. Accordingly, the invention of modulating fuel flow in relation to air temperature variations ensures the maintenance of a fuel-air ratio that is continuously closer to a selected target value than was heretofore possible.
Similarly,
In both
The term, “remote control-flow regulator”, is used herein to mean a device such as a valve or damper that is operated electrically or pneumatically or hydraulically. An electrically operated device is usually preferred for simplicity.
Of course, combustion systems use excess air to ensure complete combustion of the fuel, and importantly in lean-premixed burners, to lower the combustion temperature to minimize NOx formation. Excess air is conventionally defined as the amount of air that is in excess of the stoichiometric requirement of the fuel with which it is mixed. Good practice calls for excess air that is 15% or greater. In lean-premixed burners operating at 9 ppm (parts per million on a volumetric basis) or lower NOx emissions, the excess air level may be 65% or higher. Most of the excess air in the lean-premixed burners serves to lower the combustion temperature and hence its oxygen content acts as an inert like nitrogen to lower combustion temperature.
In as much as flue gas is warmer than air, it is thermally more efficient to recirculate some flue gas in place of some of the excess air in high-excess-air burners. This can be done as long as the oxygen-depleted flue gas is not mixed with air in a proportion that makes the mixture have insufficient oxygen for complete combustion of the fuel. Theoretically, the mass of the fresh air in an air-plus-flue-gas mixture must therefore be sufficient to provide 15% excess oxygen in the fully combusted products in order to be consistent with standard combustion practice.
Once the minimum oxygen requirements for complete combustion are met, any additional mass flow in the air-plus-flue-gas mixture can be inert (no oxygen) and still achieve the desired affect in the low-NOx burner of lowering the flame temperature. A typical air-plus-flue-gas stream could therefore be comprised of 100% stoichiometric air, 15% excess air, and flue products that have a mass that is equal to 40% of the total air flow. The total mass flow of this air-plus-flue-gas stream would be equivalent to a “61% excess air” fresh-air-only stream, and would therefore have similar flame-cooling capacity. The benefit of operating with 15% excess air and 40% recirculated flue gas, instead of 61% excess air, is higher thermal efficiency because of the heat in the flue gas.
Recirculated flue gas is commonly used in combustion systems with firing rates in excess of about 0.5 MBTU/hr (million British Thermal Units per hour). Obviously, the temperature and quantity of recirculated flue gas can cause wide temperature variations of the stream that is mixed with the fuel prior to combustion. Therefore, the invention is particularly valuable in such cases by maintaining substantially constant the fuel-air ratio that was selected for thermal efficiency and low NOx emissions.
An example of the invention as applied to the two-point parallel positioning system of
The fuel was natural gas (985 BTU per cubic foot) and an air-plus-flue-gas mass flow equivalent to 65% excess air was selected to achieve the desired low NOx emissions. The actual air-plus-flue gas mixture was allowed to vary between 65% excess air and no flue gas (as the excess air only condition) and 20% excess air and 37% flue gas (as the high flue gas recirculation condition). At 65% excess air or equivalent air-plus-flue-gas mass flow, the Alzeta CSB burner (a porous surface combustion burner) used in this example is known to yield not more than 9 ppm NOx emissions. The temperature of the air stream (including recirculated flue gas) varied between 50° F. to 200° F. as the fresh combustion air flow was decreased and the flue gas flow was increased. NOx emissions (corrected to standard 3% stack oxygen) were maintained at a level between 5 and 9 ppm.
Based on experience, without valve 21 and associated components, it is known that an air temperature swing from 50° F. to 200° F. would have caused a 29% decrease in the mass flow of the air-plus-fuel-gas stream and a 29% increase in the mass ratio of fuel to air-plus-flue-gas. Due to the very tight control requirements of ultra-low-NOx burners, this change in fuel to air-plus-flue-gas mass ratio would have resulted in unacceptably high NOx emissions.
Similarly, if the burner was tuned to operate properly at the 200° F. air-plus-flue-gas temperature, then a decrease in temperature to 50° F. would have caused a 29% increase in air-plus-flue-gas flow, and 29% decrease in the mass ratio of fuel to air-plus-flue-gas, and a probable loss of burner stability.
With valve 21 and associated components installed, the secondary fuel flow control valve partially closed to decrease fuel flow when the air-plus-flue-gas temperature increased, and partially opened when the air-plus-flue-gas temperature decreased. The change in mass flow ratio of the fuel to oxidizer stream over the full range of operation was less than plus or minus 5%. Good flame stability and sub 9 ppm NOx emissions were achieved over the full range of operation.
Microprocessor-based controller 31 in the two-point parallel positioning system of
Those skilled in the art will visualize variations and modifications of the invention without departing from the spirit or scope of the invention. For example, if it were desired to compensate also for temperature changes of the fuel, a temperature sensor would be placed in fuel line 4 and means for varying air (with or without flue gas) flow would be operated by a converter 24 that converts thermocouple signals from the temperature sensor in line 4 into a current that drives the means for varying air flow. The means for varying the air flow may be another damper like damper 7 or a valve, e.g., a butterfly valve, in air line 1 in series with damper 7. If temperature compensation of only fuel is desired, components 21 to 25 can be eliminated. A temperature sensor in fuel line 4 acting with a converter 24 and a flow regulator in air line 1 would cause the air flow to increase as the fuel temperature drops and to decrease air flow as fuel temperature rises. In short, such air flow changes are the opposites of those occurring when air temperature is monitored. Another way of compensating for fuel temperature variations is to place a temperature sensor in fuel line 4 and to pass temperature signals from the sensor to a converter that modulates the flow of fuel through an electrically operated, added valve in fuel line 4. With this arrangement of sensor, converter and added valve, a decrease in fuel temperature will cause the added valve to decrease fuel flow, while an increase in fuel temperature will result in increased fuel flow. While the example of the invention used natural gas and a porous surface combustion burner selected for achieving minimal NOx emissions, the invention is applicable to any combustion operation using any liquid or gaseous fuel and any type of flame or flameless burner. In view of the frequent use of recirculated flue gas, the mention in the claims of air, that is monitored for temperature variations, means air with or without recirculated flue gas. Accordingly, only such limitations should be imposed on the invention as are set forth in the appended claims.
| Number | Name | Date | Kind |
|---|---|---|---|
| 4249886 | Bush | Feb 1981 | A |
| 4613072 | Kikuchi et al. | Sep 1986 | A |
| 5277134 | Schlessing et al. | Jan 1994 | A |
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| Number | Date | Country | |
|---|---|---|---|
| 20040214120 A1 | Oct 2004 | US |
