| 1. | Device for supply of secondary air (10) in a boiler when burni wood or other fuels such as chips and pellets characterised by a construction in the shape of a doublejacketed truncated con of steel plate or other heatresistant material where the inne jacket (11) has a nu ber of penetrating holes, the inner and outer jackets are joined gas tight to each other at the apex and base of the truncated cone along the entire periphery of the apex and base respectively, and the space (13) thus formed between the inner and outer jacket is equipped with a number o duct connections (9) for supply of secondary air. |
| 2. | Device according to claim 1 characterised by the holes in the inner jacket being symmetrically distributed over the jacket surface. |
| 3. | Device according to claims 1 or 2 characterised by the holes in the inner jacket having a diameter of 35 mm. |
| 4. | '. |
| 5. | Device according to claims 1,2 or 3 characterised by the secondary air being conveyed by a microcomputercontrolled fan (8) to maintain somewhat overstochiometric combustion. |
| 6. | Device according to claims 1/2,3 or 4 characterised by a plate mounted over the aperture (12) formed by truncating the cone, the plate having a central hole that is small compared to the original hole. |
| 7. | Boiler (24) for using the device according to any preceding claim covering the primary combustion part (1) with grate (6,17,18) and device for supply of primary air (14,15/16), from the primary combustion part separate secondary combustion part (2,25) with device for supply of secondary air and possibly with oil (23) or gas burner, heat exchanger (20,21,22 tank for hot water etc. as well as fans, pump, ducts, pipes and adjusting equipment for air and water flow characterised by the device for supplying secondary air being placed directly above the primary combustion part sealing against the inner walls of the boiler in such a way that all gas from the primary furnace passes through the truncated cone in the direction from its base towards its apex. |
| 8. | Boiler according to claim 6 characterised by the secondary combustion part comprising the device for the supply of secondary air being housed directly in the heat exchanger. |
| 9. | Boiler according to claim 6 or 7 characterised by the walls up to the device for supply of secondary air being formed of steel plate and siliconbased flameproof material (5) lined with flameproof bricks (4) . |
| 10. | Boiler according to claim 6,7 or 8 characterised in that the tar emissions from combustion of the solid fuel are less than 5,0 g tar per MJ supplied energy. |
| 11. | Boiler according to claim 6,7,8, or 9 characterised by the soot production being less than 0,5 g soot per kg fuel and the proportion of carbon monoxide in the flue gas being less than 500 ppm calculated as a mean value over a complete combustion cycle, in conjunction with combustion of the solid fuel. |
BACKGROUND
This invention is for use with a solid-fuel-fired boiler with high combustion and system efficiency. The high level of emission and low efficiency associated with the use of solid fuels has been an obstacle to the transition from oil to solid fuels. There is a clear need for a suitable solid-fuel-fired boiler that fulfills the strict environmental and heat requirements.
A solid fuel, e.g. wood in various forms such as logs, chips, pellets or peat, differs fundamentally from oil in its combustion properties. For example, wood burns in two widely differing phases: the GAS-COMBUSTION PHASE and the CHARCOAL PHASE. Both emissions and heat are formed and emitted in two different ways. In the former phase about 80% of the fuel mass is converted to gases in a relatively short time. Thus the gas volume and the rate of emission of the volatile matter depend on an important factor, the moisture content of the fuel. High moisture levels result in a long gas combustion phase. For a conventional boiler it has been shown that the gas combustion phase is critical from the environmental and heat transfer viewpoint. There are many physical and chemical factors at work during the gas phase that affect the pattern of emissions. They will not be dealt with here. The most important factor in this context is the air supply, which will be discussed in the following.
In general the charcoal phase comprises about 20% of the total fuel mass, although the combustion time can actually be longer than that for the gas phase. The charcoal phase is favourable for emissions, mainly because of the even and uncomplicated combustion. Even so, the grate should be designed and shaped correctly to maintain a high combustion efficiency.
THE INVENTION
The aim with this boiler has been to achieve effective combustio with respect to the environment and efficiency. The construction will be described with reference to: o the combustion unit, i.e. the combustion chamber and air supply system with control and adjustment units o the heat transfer unit, i.e. the heat exchanger and tank with their associated adjusting equipment.
List of figures:
Fig. 1. Construction of combustion unit.
Fig. 2. Detail of secondary air supply.
Fig. 3. Rate of emission of volatile matter for 7,0 kg of birch containing 12% and 30% water. Fig. 4. Adjustment of secondary air flow when burning dry fuel. Fig. 5. Variation in primary air.
Fig. 6. Variation in secondary air when using moist fuel. Fig. 7. Adjusting primary air for moist fuel. Fig. 8. Amount of soot as a function of amount of fuel. Test carried out with constant air flow and a fuel moisture content of about 12%.
Fig. 9. Construction of grate and primary air du - p.
Fig. 10. Location and size of primary air duct and baffles.
Fig. 11. Construction of heat exchanger.
Fig. 12. Location of heat exchanger with respect to the combusti chamber, plus connections between the heat exchanger an oil and gas burners.
Combustion is based on the so-called two-stage principle. This means that combustion takes place in two separate chambers, the PRIMARY COMBUSTION CHAMBER (1) and the SECONDARY COMBUSTION CHAMBER (2) . The primary combustion chamber is ceramically insulated with flame-proof brick (4) next to the chamber, and a high-quality silicon-based insulation material (5) . The low thermal conductivity of both materials at the combustion temperatures in question results in extremely small radiation losses from the jacket surface of the combustion chamber. The primary air is conveyed to the fuel bed (6) by means of a
microprocessor-controlled fan.
The entire fuel mass (7-12 kg of logs depending on the moisture content) is ignited, and the primary air flow adjusted to give under-stochiometric conditions in the primary combustion chamber. Thus this can be regarded as a pyrolysis stage, where the pyrolytic gases are characterised by a severe oxygen deficit and high levels of combustible gases, mainly carbon monoxide and various hydrocarbons.
One to three minutes after ignition in the primary combustion chamber the combustion temperature becomes sufficiently high for the pyrolytic gases in the secondary combustion chamber to SELF IGNITE by additional oxygen being conveyed in the secondary air. The secondary air is driven to a mixing zone (7) by a secondary-air fan (8) through two ducts (9) and a double-jacketed device in the shape of a truncated cone. The inner and outer jackets are concentric and joined gas tight to each other along the whole periphery of the top and-bottom of the device, i.e. both the large opening to the primary combustion chamber and the smaller opening formed by the truncation. The diameter of the latter opening is determined experimentally and has been shown to be important for the function of the secondary combustion stage. Large diameters result in delayed or unsatisfactory ignition, while small diameters cause high velocities through the hole which leads to the flame being blown out or can give rise to pulsating combustion, i.e. intermittent ignition and extinguishing of the flame. The inner jacket is perforated with a large number of symmetrically distributed holes 3-5 mm in diameter.
Owing to the high pressure generated by the secondary air fan, air jets of high velocity are obtained. The result is a secondary air flow of high pressure directed to the top of the flame, which balances the pressure generated from the primary air fan. This leads to effective mixing of the oxygen and the combustible gases, as well as longer residence time of the gases in the combustion chamber. At the mouth of the device (12) burns a small gas flame whose height is adjusted according to the pressure difference between the secondary and primary air fans.
Tne neignt ot the flame in the secondary combustion chamber normally varies between 10 and 30 cm, depending on the amount of fuel and its moisture content. The volume and height of the secondary combustion chamber are chosen so that the flame never comes into direct contact with the water-cooled boiler walls of the convection part.
There is another important advantage with the double-jacketed conical detail. In spite of the high pressure pertaining in the enclosed space (13), the secondary air has a relatively long residence time. This means that the secondary air is warmed up considerably before it takes part in the combustion. Quicker and easier ignition of the combustible gases is thus obtained, together with more favourable emissions. Because of the high combustion temperatures in the secondary combustion chamber, heat-resistant materials have been chosen for the above-mentioned part.
The secondary air fan is also electronically controlled. The set values have been determined experimentally and are dependent on the amount of fuel (supplied power) and its moisture content. The reason for adjusting the secondary flow is to maintain optimal conditions for emissions and efficiency. It has been apparent from tests under normal running conditions that the optimum point is at a carbon dioxide content of around 18%. This consequently results in somewhat over-stochiometric conditions, with a mean air excess of about 20%.
Fig. 3 shows a typical curve of the velocity of volatile matter, dm/άt (kg/s) , as a function of the combustion time, t (min) . The velocity of volatile matter is determined by weighing the fuel mass at various times. The test is carried out under similar combustion conditions. These parameters have been established for all relevant service conditions and are fundamental for establishing the optimum flow, and in particular the secondary air flow. The curve in Fig. 3 is used to calculate the theoretical oxygen requirement needed to maintain complete combustion. The oxygen supplied to the flame, i.e. the secondary air flow, increases in time with the increase in volatile matter. This is shown schematically in Fig. 4 for the secondary
air flow and in Fig. 5 for the primary air flow when burning dry fuel. When using moist fuel there are fewer emissions, which means that less air and fewer adjustment stages are needed. Fig. 6 and 7 show the air adjustment when burning moist fuel.
The functioning of the boiler and even the emissions are almost independent of the moisture content of the fuel, but it has been shown that optimum efficiency and emission occur when the fuel contains about 25% water. The induced power of the boiler is determined by the distance between the lower part of the device, indicated by D in Fig. 1, and the grate (6) . For each boiler size, i.e. a boiler of specified power, there is a lower limit for the amount of fuel needed for optimum performance. This means that the after-burner stage must be functioning for the emissions to be kept down.
Fig. 8 shows how the soot formation varies with various amounts of fuel for a specific boiler size (20-30 kW) . It can be stated from this that less than 6 kg of fuel should not be used. The other emissions, such as carbon monoxide and hydrocarbons, behave in a similar way. The reason for this is that with small amounts of fuel the ignition in the secondary combustion chamber is delayed or insufficient. For amounts of fuel between 6 and 10 kg combustion is satisfactory, which suggests that the output can be adjusted within a wide range.
For effective combustion in the grate both the amount and pressure of the primary air must be evenly distributed over the whole surface without the removal of ash being affected. A number of grooves (14) have been cut in the primary air duct (15), perpendicular to its longitudinal axis, to a depth of half the diameter. An even distribution of air over each groove is achieved by means of baffles (16) giving increasing constriction with increasing distance from the supply air fan. The degree of constriction is determined partly by measuring the pressure drop across the baffles and partly by tests with smoke which is introduced into the combustion air.
The grate is constructed in three parts: a horizontal base grate (17) next to the supply air duct and two side grates (18) whose dimensions and in particular the angle of inclination, α, have been determined experimentally.
As pointed out earlier, the primary air supply is of minor importance during the gas combustion phase but not during the charcoal combustion phase. By means of the two inclined side grates the charcoal residue is successively collected on the horizontal grate. Fitting the side grates with guide vanes (19) directs the primary air onto the charcoal. Since the charcoal residue is collected on the horizontal grate the pressure drop increases and the greater part of the primary air will pass through the sides. Thus the intense combustion of the charcoal is maintained at high temperatures and levels of carbon dioxide, which favours the combustion efficiency.
The heat exchanger is designed so that the heat transfer can be fully exploited during both the gas and coal combustion phases. When the secondary combustion chamber is in use, the heat transfer occurs by both convection and radiation, while it is mainly convective in the final phase. The heat exchanger is designed to provide a single-family house with hot water (for both space heating and hot-water supply) . The volume of hot water should be sufficient for one day, even at the design outdoor temperature. The heat exchanger is the so-called through-flow type. Thus there is continuous circulation of water during a combustion cycle. The heated water is stored in a tank connected to the heat exchanger.
The open cylindrical part of the heat exchanger (20) is placed above the secondary air device, thus forming the joint secondary combustion chamber (2) , (25) so that flaming can be maintained effectively. The flow conditions between the primary and secondary air flow are adjusted to avoid direct contact between the flame and the surfaces of the heat exchanger. The hot flue gases first pass through a number of pipes ' (21) and are then led down through further pipes (22) . The surface of the heat exchanger has been designed by applying a mathematical model. The combustion temperature in the secondary combustion chamber is high and very dependent on the amount of fuel, air flow and moisture
content of the fuel. With a relatively dry fuel the temperature in the secondary combustion chamber can go up to more than 1200°C Because of this, the surface of the heat exchanger is relatively large. However, this is a stipulation if the efficiency of the system is to be at a favourable level.
Since the boiler is to be fired with fuels of varying heating values and combustion properties, automatic adjustment has been developed for the boiler water. This means that optimum efficienc is maintained under different running conditions. The electronic control unit adjusts the water flow by controlling the speed of the pump and by means of a temperature sensor placed in the supply line. The water flow through the heat exchanger has been determined by means of the temperature after the convection part. This temperature is adapted to the quality of the fuel and in particular to prevent condensation on the surface of the heat exchanger and the flue gas duct. The heated boiler water is stored in a tank whose volume is in accordance with the heat requirements of the building. However, as pointed out already, it is an advantage to fire once or maybe twice a day from the point of view of economy and convenience. The tank is not described here, since it will be a conventional tank. Of course, it can be equipped with electrical heating, which can be used when the heat requirements are low or there are economic advantages. One advantage of constructing the boiler as two separate units, i.e. the heat exchanger and the combustion chamber, is that the heat exchanger can be used as an oil-fired or gas-fired boiler. An oil burner (23) can be connected to the heat exchanger as shown in Fig. 12. As is known, the flue gas temperature with oil firing should not drop below about 200 C after the convection part. However, owing to the adjustment system for the boiler water, this can be easily achieved by arranging a suitable water flow.
Refined solid fuels such as pellets (of wood or peat) , briquette and chips have been tested by connecting a conventional feed device. The results suggest that both emissions and efficiency are better than with combustion of logs, mainly because of the continuous combustion.
Regarding the emissions, it should be noted that the National Swedish Environment Protection Board has proposed that tar emissions from small solid-fuel units should not exceed the limiting value of 10 mg/MJ. Tests conducted under various combustion and running conditions indicate that this stipulation is met by this invention. During normal running and with fuel containing 10-30% water, the tar level in five out of ten tests was measurable and less than 5,0 mg/MJ, while the condensate in the rest of the cases was completely tar free.
3 The soot concentration is generally less than 50 mg/m of dry flue gas, which corresponds to a soot quantity of around
0,5 g/kg fuel, see Fig. 8. This is considerably lower than the limiting level recommended by the National Swedish Environment
Protection Board. The levels of carbon monoxide and hydrocarbons are also low. The mean concentration of carbon monoxide from a complete combustion cycle is less than 500 ppm. It should be noted here that the carbon monoxide level during the flame combustion phase is between 100 and 150 ppm.
Next Patent: HYDRAULIC FRICTION HEAT GENERATOR