WO2006086814A2

WO2006086814A2 - Replacing fossil heating oil with liquid renewable fuels, methods, measures and device for converting heating/burner systems

Info

Publication number: WO2006086814A2
Application number: PCT/AT2006/000058
Authority: WO
Inventors: Georg Michael Ickinger
Original assignee: Georg Michael Ickinger
Priority date: 2005-02-16
Filing date: 2006-02-16
Publication date: 2006-08-24
Also published as: WO2006086814A3

Abstract

The inventive method relates to a conversion, in an extremely simple manner, of a heating system for heating oil to renewable liquid fuels, for example, purified raw glycerin, during which the burner is refitted with pulsed injectors, the heating chamber being provided with an evaporator chamber made of sintered material or fiber metal. The burner is heated by contact heat from the evaporator chamber. The burner is switched to a partial load and start-up operation via computers. The flue is converted to a flue having a concentric waste gas pipe including water separation and a purifying filter, and the tank is filled with a protective gas. The heated injectors are also used for introducing additives, reagents or catalysts into reactor chambers, e.g. during the production of hydrogen. The targeted heating of the injector nozzle leads to the increase in the heat content in propellant or fuel to an optimal combustion or reaction. The inventive method also involves: heating and increasing the pressure of the fuel; adding additives that lower the flash point; regulating the quantity of fuel by a proportional valve or pulsed injector, and; purifying the fuels by using a high-pressure filter. An anti-swirl device is employed during the supply of combustion air.

Description

Replacement of fossil fuel oil with liquid renewable fuels

Procedures, measures and devices for the conversion of heating, burner systems

The present development has set itself the task of replacing the simple heaters fuel oil extra light in homes with renewable energy to enable.

Existing EU legislation requires mixing at least 5.75% of biodiesel with fuels by 2010. This will be equivalent to 11 million tons. The long-term goal will be the conversion of these fuels to renewable energy.

This means that fossil diesel, which is obviously not identical with the fuel oil, will always be scarce and expensive. Also, those materials that are used to make substitute fuels for gasoline and fossil diesel will always be priced high to meet the blending targets or overall conversion goals.

It's easy to understand that "BIO Diesel's burning" is not and will not be meaningful and economical.

In the search for liquid renewable BIO fuels (hereinafter referred to as FEB), GLYCERIN purified from crude glycerine offers purified BIO oil prepared by pyrolysis of wood, purified distillate residues from bio refining.

Furthermore, the focus of the considerations will be on purified GLYCERIN.

Raw glycerin is 8% waste in the BIO Diesel production process. Whatever the use of BIO diesel products, there is currently no economic use of crude glycerine except for pharmaceutical glycerine and replacement of glycerine derived from fossil fuel.

The refining of crude glycerine is too expensive.

Raw glycerol burns badly is hardly inflammable. (Flame retardant, water content) Pollutants are produced that make an approval impossible. Particulate matter that makes an approval unthinkable. The minimum of 20% water content leads to poor efficiency

The present concept presents an alternative to the use of glycerin as a liquid renewable fuel for residential heating rather than inferior to using raw glycerine in BIO gas plants or power plant firing.

In the following discussion, let us assume that the above disadvantages of the high cost of cleaning can be solved. Subsequently, the NEW state of the art is considered.

This consists of:

Logistical supply and market for FEBs.

Purity of the type of heating with regard to exhaust emissions and particulate matter discharge in FEBs.

Influence of energy supply on type of heating: calorific value <-> transport, logistics.

Influence of purity on the type of heating. Influence of the flexibility of the heating system on the type of heating.

Influence of the partial load capacity of the heating system on the type of heating.

Improvement of the calorific value to the condensing boiler.

Improvement due to low heat requirement: "passive house".

Heat consumption with expected technical improvements

Influence of energy supply on type of heating: calorific value <-> transport, logistics

Transport costs are still an important cost factor when considering the cost-effectiveness of heating systems.

Location to the supply centers depending on the type of fuel

It is the relationship of the transport costs and the type of heating in distance from

City and metropolitan areas to consider. District heating systems require at least two insulated thick pipes.

The sphere of activity is therefore close to the city centers.

Natural gas requires only one - in comparison to the heat of the heat - thin pipe.

The effective range is located at the main strands with a longer range.

Fossil fuel oil and gas transports are currently the economic alternative to remote areas and are therefore served nationwide.

Pellet heaters depend on the distance of the pelletizers.

Wood heating systems have the lowest impact of self-catering transport costs, but have a low degree of automation.

Both transport mode, storage and storage differ significantly with liquid or solid fuels.

Today, pellet heaters provide almost similar modes of transport as liquid fuels by means of blowing. The storage room is twice as big as heating oil. The drying of the pellets must be guaranteed.

The prerequisite for the following consideration is the assumption that there is district heating, long-distance gas from "renewable" energy, and that there is a real BIO alternative to extra-light fuel oil.The logistics supply is identical to that of fossil fuel oil Weight unit larger, but about the same size as the pellets.

Below is the specific calorific value in terms of weight and volume

- A -

At the same calorific value, pellets and glycerin are equal in weight and have three times the weight of heating oil. With regard to storage space, double the volume is required for glycerol and four times more for pellets compared to heating oil.

Concerning possibility of cleaning of fuel wood and pellets are limited because of firm consistency. Exhaust emissions and particulate matter discharge in solid fuel heating systems are already well above the permitted limits.

Influence of purity on the type of heating:

The regulations on approvals of heating systems have led to the removal of impurities such as sulfur, phosphorus and fine dust formers with extremely complex processes for extra-light heating oil and natural gas at great expense. For wood and pellets, there are currently no possibilities for cleaning. It is very possible to achieve chemical as well as mechanical cleaning with liquid fuels and to adapt to the requirements of the environmental conditions.

Influence of the flexibility of the heating system on the type of heating In comparison with today's engine control systems today's heating systems are not on the state of the art. Improvements up to 25% are possible.

The regulations for approvals of heating systems will mean that contaminants such as sulfur, phosphorus and fine dust formers will have to be removed with great effort, even with liquid BIO heating fuels, with very complex procedures. Here you are compared to oil and natural gas just at the beginning of the process. The efforts of the plant manufacturers for BIO Diesel are endeavored to achieve a utilization of glycerine in order to improve the overall efficiency.

Influence of the partial load capacity of the heating system on the type of heating Improvement of the efficiency by burner system:

The manufacturer's information on the performance of the heating system is given in each case to the continuous operating condition. This requires a period of about 20 minutes to start up the heating system under less than optimum conditions. The systems offered today only know two states: Heating ON <-> OFF. (There are medium sized plants designed for two stages of combustion).

Now the combustion and exhaust gas values of these small plants are much worse than the values of the optimal continuous operating condition.

Comparing today's heating systems with automotive engine control systems, the "Middle Ages" prevail: engines have up to 40 sensors that relay the states of air, exhaust, engine temperatures to the engine computer, which controls the operating values of air, fuel and combustion.

The introduction of the COMMON RAIL system with the associated engine control system has brought fuel savings of more than 25%. This is also to be expected for heating systems.

Improvement of the calorific value to the condensing boiler

Today, there are still numerous incinerators with outdated chimney systems.

These systems may only be operated with exhaust gases greater than 100 ⁰ C, otherwise

Water vapor in the fireplace condenses and the moisture destroys the fireplace (sooting). The water along with the acidic or basic impurities destroys the exhaust pipes.

Today's condensing heating systems consist of two concentric tubes.

The inner tube is made of stainless steel and leads the hot exhaust gases to the outside. The old existing chimney pipe is used to supply the fresh air. This arrangement is used to use the exhaust heat, which is supplied from the exhaust gas of the fresh air.

There are now the following advantages:

- The exhaust gas enters the atmosphere at a lower temperature

- The heat of the exhaust gas is supplied to the fresh air and is not lost. - The heat of evaporation of the water in the fuel is recovered.

(the heat that must be added to evaporate the water). Condensing boiler

The mode of action is in the heat exchanger, which is installed as a steel pipe in the existing fireplace. The exhaust gas flows out through the steel pipe and releases the heat to the incoming fresh air.

The exhaust gas is thus cooled from 150 ⁰ C to 60 ⁰ C. In addition, the water vapor is condensed, thus additionally giving off the heat of vaporization to the fresh air. Operation of the fireplace heat exchanger of a condensing heating.

Improvement due to low heat requirement: "passive house"

Today, the energy consumption of an energy-saving house is around 5000 kWh, which corresponds to an energy requirement of 18 GJ / a.

Compared to the current average energy consumption of 20,000 kWh / a in the current residential building, this is a quarter.

This 72 GJ / a corresponds to a fuel oil extra light demand, assuming a calorific value of 0.6 of

72000/43 x 0.6 = 2790 liters of heating oil per year (includes electricity for hot water ...)

Heat consumption with expected technical improvements

Summing up the technical improvements of the previous novelties, the following values are obtained: Improvement of the heating system in the partial load range 25%

- Introduction of the calorific value boiler system 20%

- Partial improvement towards PASSIVE HOUSE 10% Total expected consumption 0.75 x 0.8 x 0.9 = 54%

Taking into account the technical development, we will need slightly more than half of the heating fuel in the future. Outlook for BIO Heizstoffes

Glycerol availability by current occurrence

(in relation to biodiesel) a) Austria has 11 plants producing biodiesel 100-OOOt / a. (Dl Dr Joseph Stamp Biomass Conference Excursion I).

After 10 l of biodiesel as a by-product 1t glycerol drops this is 10,000 t / a. b) Germany produces 1, 000,000 t / y biodiesel in 2003.

(Biomass Conference Doc. Werner Koerbitz, Austrian Biofuels Institute). That's 100,000 t / a of glycerine in 2003. c) Western Europe (EU15) produced about 1, 900,000 t / a in 2003.

(Biomass Conference Doc. Werner Koerbitz, Austrian Biofuels Institute). That's 190,000 t / a of glycerine in 2003.

Glycerine Maximum available potential

a) The primary energy requirement of Austria speaks of 15% diesel for transport If this diesel was produced entirely as biodiesel, this would amount to one tenth of the mass as glycerine.

17 MJ / kg glycerol compared to 43 MJ / kg for fossil fuel oil Maximum glycerin would be (15% x 17) / (10 x 43) = 0.6% of the total energy.

This corresponds to 0.6% x 100/57 = 1.0% of the total fuel quantity of energy.

b) In 2001, primary energy for Austria amounted to 1290 PJ (Document 'Renewable Energy in Austria' from www.bmwa.gv.at).

Thus, the calorific value of glycerol is 0.6% x 1290 PJ = 7.74 PJ = ~ 8 PJ / a.

Assuming that an existing house needs 72 GJ / a, 100,000 houses and a passive house 18 GJ / a needed, 400,000 houses can be heated. Cost comparison of heating fuels.

('Regional Energy Steiermark' Biomass Conference). Assumption 10 kW heating, efficiencies without hot water in the summer heating oil EL, incl. Delivery charge 0.490 € / 1 Lower calorific value is 43 MJ / 1 The costs are Khö = 0.49 x 3600/43 MJ = 0.0407 € / kWh. Pellet injected, 165 € / 1 Lower calorific value is 17 MJ / kg The boxes are Kpe = 165 x 3.6 / 17000 = 0.035 € / kWh

Glycerin 30 to 60 € / 1 price of biodiesel plant in Mureck)

Lower calorific value 17 MJ / kg efficiency 0.8, without refining costs. The costs are KgI = (60 x 3.6) / (17000 x 0.8) = 0.016 € / kWh.

Thus, the cost of glycerin heaters is one quarter of the pellet.

Need for residential buildings of liquid BIO heating fuels

Assuming that about 400,000 heating systems are outside the district heating, gas and pellet heating.

If one considers the energy calculation with the possible coverage of this requirement for heating fuels for liquid BIO heating fuels by means of GLYCERIN.

Taking into account that according to new technologies only half of the energy demand will be necessary, one can draw the following conclusions for the heating of residential buildings:

A conversion of heating oil heating systems is possible and useful. It is not necessary to increase the number of tanks. Glycerin has half the calorific value of the volume. The conversion costs are related only to the burner and the conversion from calorific value to calorific value heaters (heat exchangers in the chimney) is a requirement for the purity of glycerine because of environmental regulations

Combustion system for flame-retardant liquid fuels

Europ Classification F23C1 / 00

Liquid burners in conventional heating systems rely on a fan-generated turbulent air flow of a fuel oil-diesel or biodiesel pump for maximum 40 bar pressure generation and a centrally located burner nozzle together with an electronic control unit. The atomization achieved thus far does not permit combustion of flame retardant fuels, e.g. Glycerine in compliance with the emission regulations. Method:

The method described here is characterized in that by means of a high-pressure injection system, the hardly inflammable fuels are so atomized and mixed with air, so that an efficient combustion takes place.

The process should continue with the easy conversion of existing heating systems

Combustion of liquid fuels.

The following measures are proposed for this purpose.

1. Pressure increase and heating of the fuel over the flash point.

2. Regulation of fuel quantity by proportional valve or pulsating injector.

3. Addition of flash point lowering additives

4. Cleaning of the fuel by means of a high-pressure filter

5. Optionally, an admixing system for additives against flooding 6. counter-twist device in the combustion air supply

1. Pressure increase and heating of the fuel over the flash point.

The basic idea behind the atomization of flame retardant fuels is that the temperature of the liquid in a sealed pressure system is heated above the flashpoint at more than 40 MPa.

This pressure range is necessary to suppress the boiling of flame retardant fuels prior to injection.

2. Regulation of fuel quantity by proportional valve or pulsating injector. By means of a suitable proportional valve or controlled pulsating injector, the heated fuel is now injected into the combustion chamber and swirled with air. Subsequently brought to combustion. The valve also controls the required amount of fuel.

3. Addition of flash point lowering additives

As an additional measure for the ignition of flame retardant fuels admixture of additives is proposed, which reduce the flash point of the fuel - at least when starting the heating system.

This would be e.g. for glycerine, the admixture of methanol and liquid soap can be implemented.

4. Cleaning of the fuel by means of a high-pressure filter

By means of coarse filter in the low pressure range and molecular filter in the high pressure range, the delivered fuel is cleaned. After binding any ions such as KOH or NaOH, the impurities are eliminated.

5. Optionally an admixing system for additives against flocculation

For example, phenol monomethyl ether or topanol in bio oils

6. counter-twist device in the combustion air supply

As an additional measure for better flame formation, the supplied

Combustion air supplied in two concentric tubes having means for swirling and this twist has opposite directions of rotation in the inner and outer tube. The purpose of this device is to create a fluidized bed at the confluence of these opposed air swirls through which must pass through fuel injected at high speed. It comes to delay the residence time and good mixing with the combustion air. State of the art for the incinerator

Ad 1 pressure increase of the fuel for heating above the flash point

The author is currently no means for increasing the pressure of the fuel for the purpose of heating known as the prior art Ad 2 Regulation of Brennstoffmenqe by proportional valve or pulsating injector

EP0454351 The present device differs from EP0454351 in that no diesel fuel is used, but flame retardant fuels. In a high pressure part, these are heated substantially above the flash point.

DE10007164 and US6402505 JP2000304210

The present device is different from US6402505 in that the injected fuel does not pass through a baffle plate in the inlet opening when it enters the combustion chamber, but enters the combustion chamber directly through the heating of the fuel in the high-pressure part substantially above the flash point in the vapor state and is gas-like state.

The high-pressure injection results in addition to the good atomization and the disadvantage that a difficult ignition state can be produced by the rapid exit velocity. US6402505 solves this through the baffle plate and slows down the entrance. The present device introduces into the combustion chamber ignitable vapor above the flash point and thus uses despite high entry velocity the full ignition effect.

US6174160

The present device is different from the preheating compared to US6174160 in that the injector itself is heated and the fuel is heated in the injector before exiting substantially above the flash point.

WO0151267 GEORG (CKINGER 1999

The present device differs from this in that the injector is heated and measures are taken to improve the flammability of the fuel

WO 2004055437

The present device is distinguished from WO2004055437 in that the injector is heated and measures are taken to improve the flammability of the fuel. Ad 3 admixture of flash point lowering additives

There are Selbstentzündliche fuel mixtures for diesel engines, which are also used in boilers. WO0112756 WIEDERMANN, HOUSES, TOMBERG FEB-2001

Glycerol: 25-70%, soaps: 5-40%, water: 3-25%, methanol: 0.1-50% Indicated in weight percentages based on the sum of the four components.

WO9525152 NYLUND NILS-OLOF 1995

FR2496119 GUIBET JEAN-CLAUDE 1980

The foregoing WO0112756, WO9525152, and FR2496119 relate to internal combustion engines. The present invention relates to an incinerator.

Twist device at the combustion air supply

US20040177611

The present device is distinguished by US20040177611 that two mutually moved twisted air flows move towards each other and form a fluidized bed, in which - due to the heating in the injector - vapor strikes and comes to turbulence.

Behθizte injectors for injection in combustion chambers and reactors

F02M53 / 02, / 04 Fuel-injection apparatus characterized by having heating. The aim of the device is the heating of the blowing additive or fuel gas mixture at flash point or ignition point temperature for the purpose of combustion in engines, or boilers or introduction into reactors. Especially with fuels or fuels with lower calorific value and higher flash point, this device is used for better ignition and economical combustion. Reactors for the production of hydrogen gas

The targeted heating of the injector leads to increase the heat content of the fuel or propellant, and in turn in connection with the preheated air to increase the temperature of the fuel or fuel mixture.

To illustrate, the following calculations are used for each of an internal combustion engine or boiler for diesel or glycerine as a fuel: The following figures serve as a basis for calculation.

Calculation for the diesel engine with glycerin:

With 374 ° C temperature of the fuel-air mixture it comes only to the ignition with glycerine, if this is preheated to at least 300 ⁰ C. With no preheating the ignition point is not reached. Calculation for the diesel engine with diesel:

In diesel auto-ignition (as well known) is achieved without preheating the fuel.

Calculation for the boiler with glycerine:

Without preheating of glycerol to at least 200 ⁰ C, the flash point of 199 ° C from

Air and glycerine not reached. Even by spark ignition, the combustion start is not possible.

The trivial calculation for fuel oil is spared here, since at a flash point of 65 ° C already an air heating of about 80 ⁰ C without diesel preheating is sufficient to the

To ensure spark ignition.

The preheating of fuel or fuel to the above temperatures is only possible under high pressure and under exclusion of air, as is generally in the liquid diesel and biodiesel and liquid fuels or heating and fuel or the flash point above the boiling point and the heating must therefore be carried out under pressure in order to avoid premature boiling in the injection system.

In general, the pressures in the injection systems are above 40 Mpa, so this requirement is met. The high temperatures of the nozzles of injection systems are given in today's engines and the nozzles have proven themselves over a long service life. The radiant heat in the diesel engine heats the nozzle needles to over 500 ^° C so that this area of the injector can be exposed to these temperatures.

The heating of injectors presented here is carried out by the following methods: Electric heating element, heating loop in the starting phase. Heat transfer through jet plate at the nozzle. Flushing of the nozzle by exhaust gas flow to the exhaust valve. Flushing of the nozzle by means of exhaust gas in the pipe system.

Measures to increase the heat transfer within the nozzle to the fuel or fuel.

Electric external heating in the starting phase.

By means of ohmic heating, the injector is externally heated in the lower area.

Heat transfer through jet plate at the nozzle.

In the combustion chamber, a heat-insulated from the combustion chamber radiant panel is pressed with good metallic contact on the nozzle. The radiation from the combustion chamber is conducted into the radiant plate and from there by means of heat conduction to the nozzle.

Flushing of the nozzle by exhaust gas flow to the exhaust valve. The front portion of the injector, in particular the nozzle, projects into the exhaust stream and is supplied with heat for transmission to the fuel.

Flushing of the nozzle by means of exhaust gas in the pipe system.

For boilers, the injector by means of looping pipeline, the hot combustion air from the combustion chamber the injector for convection introduce. For the start of the heating system, the nozzle is electrically heated.

Measures to increase the heat transfer within the nozzle to the fuel or fuel. Between the nozzle needle and the nozzle body, the surface of the interior of the nozzle body is increased by means of electroerosion, characterized in that the cross section has a splined shaft profile. The following calculation is roughly given: Fuel: Glycerol with the specific heat of 2.43 KJ / kg,

Fuel quantity in the boiler 2kg per hour at continuous full load operation. Heating surface inside the nozzle body 5cm ² corresponds to 0.00005m ² temperature difference of 480 ⁰ C nozzle body to 180 ⁰ C mean temperature is equal to 300 ° C heat transfer bare metal to liquid at high pressure: 8000 KJ / m ² hgrd The following heat is transferred: 8000 x 0.0005 x 300 = 1200 This results in a heating of dT = 1200 / (2x2.43) = 244 ⁰ C Assuming that the glycerine enters the nozzle area at 56 ° C and leaves with approx. 300 exits a mean temperature difference of 300 ⁰ C. Heating at full load is given. At partial load, a lower radiant heat is transmitted and thus also lower heating of the set by lowering the temperature difference. The upper part of the injector is kept cool in all the previously proposed heaters in order not to overheat the leak oil from the servo, since this substance is returned to the radial pump and evaporation or decomposition is undesirable.

State of the art for heated injector

WO03083283 PELLIZZARI ROBERTO O

The present device is different from WO03083283 in that before entering the combustion chamber, it does not have a capillary, as here, but with a capillary

Valve needle creates a high pressure state in the injector, so that there is no formation of vapor.

The vapor formation takes place only when entering the combustion chamber.

US6174160 LOHN LEE 2001 The present institution is different from

US6174160 in that the vaporous fuel is injected directly into the combustion chamber and not differently heated chambers flows through.

US 4396372

The present device is distinguished from US 4396372 in that the closure element is arranged in front of the combustion chamber and not in front of the heating device as in US Pat. No. 6,174,160. Description of the figures:

Reference numeral directory:

1. Fan for combustion air

2nd injector

3. High pressure fuel supply

4. Heat exchanger hot air feed

5. Swirl device inner tube 6. Swirl device outer tube

7. Nozzle body optionally with heating

8. Vortex left-handed and right-handed injection area

9th flame zone

10. Combustion chamber 11. Admixture additive for anti-flocculation additives

12. Additives against flocculation

13. Fuel tank

14. High-pressure pump (radial pump with torque-controlled drive)

15. Return line from the servo - actuation of the injector 16. Feed line to the high pressure pump

17. Low pressure fuel pump

18. Additive - pump for flash point lowering additives

19. Flash point lowering additives

20. High pressure filter 21. Leakage oil line servo

22. Servo control

23. High-pressure feed

24. Injector

25. Leakage oil pipe Control needle 26. Control needle

27. Leakage pipe nozzle needle

28th nozzle needle

29. Supply of fuel or fuel

30. Nozzle body 31. Injection opening (s)

32. Servo cooling zone 33. Mean temperature zone

34. Injection side heating zone

35. Supply line servo

36. Cylinder head 37. Inlet valve

38. exhaust valve

39. Radiation plate

40th outlet channel

41. combustion air supply 42. heat transfer

FIG. 1 shows a high-pressure injector from WO 0151267 during the introduction of fuel into the combustion air stream. FIG.

Figures 1 and 2 show the high pressure injector

1. Pressure increase and heating of the fuel over the flash point.

2. Regulation of fuel quantity by proportional valve or pulsating injector.

3. Addition of flash point lowering additives 4. Cleaning of the fuel by means of high pressure filter

5. Optionally an admixing system for additives against flocculation

6. counter-twist device in the combustion air supply.

In FIG. 1, the

Injection system consisting of fan for combustion air (1), injector (2), high pressure fuel supply (3), heat exchanger hot air supply (4) swirl device inner tube (5), swirl device outer tube (6), nozzle body, optionally with heating (7), vortex left-turning and clockwise, injection area (8), flame zone (9), combustion chamber (10) shown. The supplied hot air (4) is used to heat the injector in the area of the nozzle and is insulated by means of constriction of the servo operating part of the injector (2) thermally, so that the operating mechanism is not exposed to high temperatures.

In the inner tube there is a twisting device (5) which in this case provides the hot air (4) with a right twist. In the outer tube is - by means of twisting device (6) - the combustion air (1) provided in this case with a left twist. In the area of injection (8), the turbulent layers of right-hand spiral (4) and left-hand spiral (1) now come together. In this layer, the turbulence will now take place before the fuel mixture penetrates into the flame zone (9) and burns in the combustion chamber (10).

FIG. 2 shows the incinerator. Combustion air (1), injector (2), high-pressure fuel supply (3), anti-entrainment additive pump (18), anti-entrapment additives (19), fuel tank (13), high-pressure pump (radial pump with torque-controlled drive) (14), return line from the servo - operation of the injector (15), supply line to the high pressure pump (16), low pressure fuel pump (17), admixture - pump for flash point lowering additives (11), flash point lowering additives (12) shown.

The circulation of the fuel in the high-pressure region takes place after being fed by the low-pressure pump (17) and passes via the high-pressure pump (15) for feeding the injector (3) to the injector. There, the nozzle body and the servo control panel are supplied with fuel. The return from the amount of fuel necessary for the operation of the servo is returned via the drain line (15) in the low pressure range. An admixture by the pump 18 of flash point lowering additives (19), as well as the cleaning of the fuel by means of high pressure filter (20) and the optional admixture with the pump (11) of additives (12) against the entangling are shown. The prior art shows the two-circuit injector

Figure 3 shows the injector with preheating for fuel or fuel Figure 4 shows the use of the injector in the cylinder head with radiant panel Figure 5 shows the use in the exhaust stream

Figure 6 shows the injector with radiant panel in the combustion chamber of a boiler Figure 7 shows the injector with heat conduction from the combustion chamber

For the prior art from WO0151267 a two-circuit nozzle consisting of

Leak oil line servo (21), servo control (22), high-pressure feed (23), injector (24), drain line (25), control needle (26), drain line (25), nozzle needle (28), fuel or fuel supply line (29), nozzle body (30), injection port (s) (31), one of which concerns the injection medium and the second circuit supplies the servo operation.

FIG. 3 shows the dual-circuit nozzle in an extended function

The present device extends the function by heating the injector in the two circuits. The area Servo (32) should be as unheated work area as possible The middle area (33) consists of the heat transfer zone. The injection area (34) consists of the nozzle body and the lower injector area and is heated intensively in order to achieve heating of the fuel or fuel in one pass through the injector. This concerns the heat transfer in the areas (33) and (34). 7 shows the leakage of the leak oil at the nozzle body. At these temperatures of 300 ⁰ C and pressure above 40 Mpa hot fuel will escape between the nozzle needle and the nozzle body. Advantageously, this should be performed in the combustion chamber and not return to the high pressure circuit. For this reason, there is also a seal in the middle region (33).

The amount of leakage oil between the actuating needle and the servo cylinder is sealed by means of a seal against the exit into the combustion chamber and returned to the low-pressure region (25). From there it gets into the drain line of the servo (21) FIG. 4 shows the heating of the injector (24) by means of an example on the cylinder head (36). The nozzle body (31) is positively pressed into the radiant plate (39) in order to achieve a good heat transfer. The radiant plate is located between inlet (37) and outlet (38) and is advantageously isolated from the cylinder head. The radiation from the combustion chamber heats the radiant panel

FIG. 5 shows an example based on the heating of the injector (24) in the nozzle body region (30) in the outlet channel (40). The attachment of heat transfer ribs to the nozzle body (30) will be advantageous.

FIG. 6 shows the heating of the injector (24) in the region of the nozzle body (30) by means of a jet plate (39) in the combustion chamber of an incinerator. The heat transfer takes place by radiation from the combustion chamber to the radiant plate (39) and from there to the nozzle body 30) of the injector (24).

FIG. 7 shows the heating by means of a heat exchanger (41) which is fed from the combustion chamber via a supply line of hot air. The heat transfer (42) takes place advantageously via heat transfer ribs on the nozzle body (30). If necessary, the middle part of the injector for heat transfer (42) is involved with high heat demand.

Claims

claims

A method of converting a heating system of heating oil extra light to renewable liquid fuels such as purified crude glycerine, wherein; the burner is switched to pulsating injector, the combustion chamber is equipped with an evaporator chamber made of sintered material or fiber metal, the burner is heated by contact heat from the evaporator chamber, the burner is switched by computer to partial load and start-up, the fireplace on fireplace with concentric exhaust pipe included Water separation and cleaning filter is changed, the tank is optionally provided with protective gas filling.

2) Combustion system for burning at least one flame retardant liquid fuel eg GLYCERIN for currently used heating systems in the power range, for example from 10 to 100kW consisting of: ^• a burner system with a high pressure injector which heats the flame retardant fuel, if necessary via the flash point optionally a heat component Mixing plant for admixing flash point-lowering additives such as: methanol, liquid soap, a molecular filter system inserted in the fuel circuit for purifying the fuel of bound ions such as KOH or NaOH from the transesterification, optionally from an admixing system for additives against flocculation, for example phenol monomethyl ether or topanol in bio oils

Combustion air supply in two coaxial tubes with means for mutually acting swirl devices.

3) A method for burning of flame-retardant liquid fuels such as GLYCERIN, characterized in that by means of heated high-pressure injector, the fuel is heated above the flash point and injected into the combustion chamber by means of a pulsating injector or proportional valve in the combustion chamber and ignited. 4) Method according to claim 3, characterized in that the high pressure for temperature control of the flame retardant fuel is chosen so that a vapor formation in the high pressure system is not possible.

5 5) A method for the separation of bound ions such as KOH, NaOH, and water from the flame retardant fuels characterized in that the fuel in the high pressure part at about more than 40 Mpa is passed through a molecular microfilter and harmful substances of the fuel from the Be pressed cycle.

o 6) method for adding at least one additive in the fuel cycle, characterized in that before the high pressure injection system by means of variable speed diaphragm pumps proportional to the fuel flash point lowering additives are added and distributed in the circulation process in the high pressure circuit.

5 7) method for combustion air supply in two coaxial tubes, characterized in that they are provided with means for swirling, which exerts a mutually acting swirl on the combustion air.

8) injection system for use according to claim 2, consisting of at least one o low-pressure feed pump, radial piston pump, pulsating injector with preheating and

Control characterized in that the radial piston pump is coupled to a torque-controlled geared motor.

9) injector for use according to claim 2, characterized in that the injector is heated at 5 nozzle body optionally by means of a heat exchanger or electrical heating loop.

10) injector for use according to claim 2, characterized in that the hydroelectric servo part is cooled by means of a heat exchanger, for example.

0 11) high-pressure molecular filter system for use according to claim 2 consisting of a filter tube with high pressure inner chamber and low pressure Aussenkammer characterized in that the filter tube is integrated into the high-pressure circuit by means of inlet and outlet and the filter tube made of sintered ceramic with pore size of 3 to 4 Angstrom and the filter tube is provided with a support structure which withstands an internal pressure of up to 140 MPa. 12) combustion air supply for use according to claim 2, characterized in that in two coaxial tubes means for swirling the combustion air is provided with mutually acting swirl, the supply means is designed such that these two air turbulence meet in the field of injection of the fuel.

13) device for heating an injector of the fuel or fuel injected into a combustion chamber or additives in reactor chambers, characterized in that the nozzle body is heated and this heat is transferred to the blowing additive or fuel.

14) An apparatus for heating an injector according to claim 13, characterized in that the nozzle body is connected to a heat transfer plate with good thermal contact and the heat transfer plate is directed into the combustion chamber with the surface almost transverse to the flame center and this heat plate against the wall of the combustion chamber isolated is to minimize heat conduction to the wall, so that radiant and Koπvektionswärme the nozzle body is supplied, and the nozzle body inside a bare advantageous by wedge-shaped training enlarged surface so that the supplied heat is transferred to the fuel.

15) An apparatus for heating an injector according to claim 13, characterized in that the nozzle body protrudes into the exhaust pipe of an internal combustion engine and is advantageously equipped with additional heat transfer surfaces, so that radiation and convection heat is supplied to the nozzle body, and the nozzle body inside a bare advantageous by wedge-shaped training has enlarged surface so that the supplied heat is transferred to the fuel or fuel.

16) Apparatus for heating an injector according to claim 13 to 15, characterized in that the nozzle body so that radiation and convection heat the

Nozzle body is supplied, and the nozzle body in the interior has a bare advantageous by wedge-shaped training enlarged surface so that the supplied heat is transferred to the fuel.

17) Apparatus for heating an injector according to claim 13 to 16, characterized in that the nozzle needle at the transition to the sealing seat a seal has the heated fuel or fuel separates from the inflowing thus exits through the sealing seat only cooler fuel or fuel as leakage oil.

18) Apparatus for cooling an injector according to claim 13 to16, characterized in that the injector is provided above the nozzle body by means of fresh air blower and the injector is kept cool in this area to prevent heating of the servo part and the leak oil line.

19) Method for increasing the mixture temperature of combustion air and fuel or fuel characterized in that the injector is additionally heated in the region of the nozzle body and this heat is supplied by means of enlarged surface in the interior of the nozzle body to the fuel or fuel to heavy flammable Treibbzw. Fuels to exceed the flash point and an ignition is simplified and the combustion is complete.

20) A method according to claim 19, characterized in that the fuel or fuel is directed in the injector in the form that hot fuel or fuel is prevented by means of measures from the leak oil points in particular at the sealing seat of the nozzle needle by sealing in the inlet region near the sealing seat or the injector body in the servo area avoids undesired heating of the leaked oil in this area by cooling