CA1080112A - Blue-flame oil burner - Google Patents
Blue-flame oil burnerInfo
- Publication number
- CA1080112A CA1080112A CA292,449A CA292449A CA1080112A CA 1080112 A CA1080112 A CA 1080112A CA 292449 A CA292449 A CA 292449A CA 1080112 A CA1080112 A CA 1080112A
- Authority
- CA
- Canada
- Prior art keywords
- tube
- flame
- oil
- air
- oil burner
- 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.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/36—Details, e.g. burner cooling means, noise reduction means
- F23D11/40—Mixing tubes or chambers; Burner heads
- F23D11/402—Mixing chambers downstream of the nozzle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
- F23D11/26—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2210/00—Noise abatement
Abstract
"BLUE-FLAME OIL BURNER"
ABSTRACT OF THE DISCLOSURE
A blue-flame oil burner including a flame-tube, a wall extending transversely of the flame-tube and defining the upstream end thereof, the wall having therein a metering orifice through which air enters the flame-tube, the orifice being the only air inlet into the flame-tube, an oil atomising nozzle positioned upstream of the wall and discharging an oil spray through the orifice into the flame-tube, and a mixing tube positioned within the flame-tube co-axially of the orifice and having its upstream end spaced axially from the wall by a distance such that the peripheral area of the space between the wall and the upstream end of the mixing tube and defined within an imaginary upstream extension of the peripheral wall of the mixing tube to the transverse wall is between one and three times the difference between the cross-sectional area at the upstream end of the mixing tube and that at the orifice, the mixing tube having a length, L, and a diameter, D, such that the ratio L/D is between 1.0 and 1.75, and the flame tube having an equivalent ratio L/D of between 2.0 and 5Ø
ABSTRACT OF THE DISCLOSURE
A blue-flame oil burner including a flame-tube, a wall extending transversely of the flame-tube and defining the upstream end thereof, the wall having therein a metering orifice through which air enters the flame-tube, the orifice being the only air inlet into the flame-tube, an oil atomising nozzle positioned upstream of the wall and discharging an oil spray through the orifice into the flame-tube, and a mixing tube positioned within the flame-tube co-axially of the orifice and having its upstream end spaced axially from the wall by a distance such that the peripheral area of the space between the wall and the upstream end of the mixing tube and defined within an imaginary upstream extension of the peripheral wall of the mixing tube to the transverse wall is between one and three times the difference between the cross-sectional area at the upstream end of the mixing tube and that at the orifice, the mixing tube having a length, L, and a diameter, D, such that the ratio L/D is between 1.0 and 1.75, and the flame tube having an equivalent ratio L/D of between 2.0 and 5Ø
Description
" 1080~1;2 The invention concerns a blue-flame oil burner, that is an oil burner intended to operate with a blue flame and having provision for recirculation of part of the combustion gases and having an oil-atomising device, a wall containing a metering orifice arranged downstream of the outlet of the oil-atom~ing device, a mixing tube arranged at a distance downstream of the orifice and coaxial with it and a flame-tube around the mixing tube.
Blue-flame oil burners require that the oil reaching the point of combustion is completely vaporised before it reaches that point. The operation of an oil burner with a blue flame has the advantage that the burner is able to operate with very small excess of air over that required for complete combustion so that practically stoichiometric combustion takes place.
Since combustion takes place with very small excess of air a very hot flame is produced which utilises the energy content the fuel optimally and leads to improved heat transfer. In addition, the waste gases in comparison with waste gases from an optimally adjusted burner with a yellow flame contain extremely little harmful material (soot, NOX, SO3).
Because of the known advantages of an oil burner in which oil is burnt in the vaporised state with a blue flame, there have been no lack of attempts to bring oil burners with blue flames on to the market.
In a known blue-flame type of oil burner an orifice plate is arranged in a double-walled combustion chamber downstream of the ~il nozzle. Oil is sprayed through the orifice plate into an ~long~te mixing tube and, with the aid of air which enters
Blue-flame oil burners require that the oil reaching the point of combustion is completely vaporised before it reaches that point. The operation of an oil burner with a blue flame has the advantage that the burner is able to operate with very small excess of air over that required for complete combustion so that practically stoichiometric combustion takes place.
Since combustion takes place with very small excess of air a very hot flame is produced which utilises the energy content the fuel optimally and leads to improved heat transfer. In addition, the waste gases in comparison with waste gases from an optimally adjusted burner with a yellow flame contain extremely little harmful material (soot, NOX, SO3).
Because of the known advantages of an oil burner in which oil is burnt in the vaporised state with a blue flame, there have been no lack of attempts to bring oil burners with blue flames on to the market.
In a known blue-flame type of oil burner an orifice plate is arranged in a double-walled combustion chamber downstream of the ~il nozzle. Oil is sprayed through the orifice plate into an ~long~te mixing tube and, with the aid of air which enters
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the tube simultaneously through the orifice, partial combustion takes place with an excess of combustible material. These -combustion gases are returned and again enter the end of the mix-ing or vaporisation tube opposite the orifice plate at the same time as the spray of fuel. In this known burner the inner wall is provided with holes through which the greater part of the air of combustion enters in the form of a secondary air flow. (Proc.
World Petr. Congr., 7th Volume 7, Sect. on Application and New Uses, Part 1, p 119 f f ) . `
An oil burner with a blue f lame with recirculation is also known in which the orifice plate is situated in a tube which exte~ds so far in the upstream direction that the nozzle and the nozzle support are situated completely within the tube. With such a burner the flame should burn immediately behind the ori-f ice plate and part of the combustion gas should be recirculated through an annular space between the tube and an outer tube (ibid).
An oil burner is also known in which oil is sprayed directly into a tuhe which is surrounded by an outer recircula-tion tube connected to the inner tube by means of bores UIC Pat-ent F18213 issued on November 10th 1954 to Thermal Research and Engineering Company.
It is an object of the invention to design a blue-flame oil burner incorporated features of ,~r~nced conventional technology and which has a high operating reliability.
According to the invention there is provided an oil burner of the kindin which vaporised fuel is capab1e of burning with a blue flame and having provision for recirculation of part of the combustlon gases within a flame tube, the oil burner com-~,..~
- 10~0112 prising the flame tube, a wall extending transversely of the flame tube and defining the upstream end thereof, the wall having therein a metering orifice through which air enters the flame tube, the orifice being the only air inlet into the flame tube, an oil atomising device positioned upstream of the wall and arran- ~
ged to discharge an oil spray through the orifice into the flame :
tube, and a mixing tube positioned within the flame tube and ~
aligned with the orifice, the mixing tube having its upstream end ~.
spaced axially from the wall by a distance such that the periph-eral area of the space between the wall and the upstream end of the mxing tuhe and defined within an imaginary upstream extension :~
of the peripheral wall of the mixing tube to the transverse wall is between one and three times the difference in cross-sectional area between the upstream end of the mixing tube and the orifice, the mixing tube having a length, L,and a cross-sectional area at the upstream end thereof equal to the area of a circle having a `~
diameter, D, such that the ratio L/D is between 1.0 and 1.75, and the flame tube having an equivalent ratio L/D of between 2.0 and 5Ø
. Preferably the ratio L/D of the mixing tube is equal ; 20 to or is approximately 1.5.
Preferably also the ratio L/D of the flame tube is between 2.5 and 3Ø
In the preferred embodiment the cross-sectional area of the mixing tube is between 1.5 and 3.0 times the cross-sect-ional area of the orifice.
The flame tube and the mixing tube may have constant cross-section over their length. For example, the flame tube and the ~" .
, 10801~Z
mixing tube may both be designed to be cylindrical.
It may,of course, be convenient for silencing to design the flame tube wlth a cross-section of varylng orm, ~or ex~mple with a conLcal enlargement or even in a star shape.
A special problem with blue-flame oil burners ls the reliable ignition of the flame in the variable starting conditions which occur in practice, for example relighting a burner which is still hot. According to a feature of the invention the necessary reliability of ignition is achieved in that the burner is started with an air pressure below that of the full-load operation. The supply of air is then quickly increased after the opening of the oil valve to an air fraction sli~htly above the stoichiometric ratio with which the oil burner is then supplied.
Operation in the manner described is preferably achieved in that the air flap of the blower is provided with a drive and that time switch means are provided for operation of the drive.
For example, an electric or hydraulic motor may be provided as the drive which is preferably connected to the air flap through a self-locking gear mechanism.
It is also possible to use an electrically excited magnetic device or a hydraulic cylinder in each case with time-controlling damping members.
It may also be convenient when starting-up either in conjunction with or instead of throttling the air supply to the burner to operate with a throttled flow of oil mixture which can then be quickly brought up to the full air-oil mixture flow.
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.: ~. :, ., lOflO11;2 By way of example an embodiment of the invention is illustrated in the accompanying drawing and is described in detail in the following with reference to the drawing, which shows a longitudinal section through an oil burner according to the invention together with its control and supply devices.
The burner 2 illustrated includes a chamber 4 in which a pressure atomising nozzle 6 is mounted in a known manner at the end of an oil supply pipe 8. Oil is fed into the pipe 8 by an oil pump 10 which is driven by a motor 12 which also drives a blower rotor 14 in a known manner. The pump 10 delivers oil through a hand-operated throttle valve 16 and an electromagnetically-operated shut-off valve 18 into the oil pipe 8 which carries the atomising nozzle 6. The blower 14 delivers air through a duct 20 into the housing 4 through a lS throttle valve 22 having air flap 24 whlch can be adjusted by a motor 26. A pair of ignition electrodes 30 is carried by a support 28 mounted on the oil pipe 8 and is connected to an ignition transformer 32.
At a distance L3 from the mouth of the pressure atomising nozzle 6 there i8 a wall 34 having a metering orifice 36 therein coaxial with the nozzle. At a distance from the orifice 36 there is a mixing tube 38 which is attached to the wall 34 by mounting rods 40. The mixing tube 38 is situated inside an outer tube 42 which forms the flame tube. In this example, the orifice 36, the mixing tube 38 and the flame-tube 4Z are circular but they need not be.
The diameter D3 of the orifice 36 and the arrangement and dimensions of the mixing tube 38 and of the flame-tube 42 are in a prdeter~ined critical relationship to each other which : ,. . ~ , :.
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` - 10801~
will be discussed in detail in the following.
The atomising nozzle 6 should be adjustable in the axial direction in order to vary the through-put of air and the oil cloud input and thus make it possible to achieve the optimum composition of the mixture.
The diameter D3 Of the orifice 36 should be chosen in such a way that at a delivery pressure of the blast 14 which corresponds to the delivery pressure normal in commercial oil ~;
burners, the air flow through the orifice 36 in the wall 34 has a predetermined velocity, the orifice being the only pas- - r sage for combustion air.
'l The diameter Dl of the mixing tube 38 is at least 1.25 and at maximum 1.7 and is preferably 1.4 to 1.45, times the diameter D3 of the orifice 36. Alternatively, the ratio of the cross-sectional area of the mixing tube and the orifice is between 1.5 and 3.0 where the mixing tube and/or the orifice are not of circular cross-section. The length Ll of the mixing tube is between 1.75 and l.ODl where Dl is the diameter of the mixing tube, and preferably Ll = 1.5Dl.
The distance L4 of the mixing tube 38 from the wall 34 is chosen in such a way that a flow cross-section, radially of the mixing tube 38, which is at least 1 to 3 times the differ-ence between the cross-sections of the orifice 36 and of the mixing tube 38 is produced between the upstream end of the mix-ing tube 38 and the wall 34. In other words, the peripheral area of the space between the wall 34 and the upstream end of the mixing tube 38 and defined within an imaginary upstream 10~0112 extension of the peripheral wall of the mixing tube 38 to the wall 34 is between one and three times the difference in cross-sectional area between the upstream end of the mixing tube 38 and the orifice 36. The diameter D2 of the flame tube 42 is approximately twice to 2.5 times the diameter Dl of the mixing tube and the ratio of the length L2 to the diameter D2 of the flame tube is between 2:1 and 5:1 and is preferably between 2.5:1 and 3:1.
A spray cone of approximately 60 to 80 degrees is convenient for the pressure atomising nozzle 6. Particularly good results were obtained with nozzles with hollow spray cones. When the oil burner is to be started, the motor 12 is first switched on inthe normal way. At the same time, the throttle flap 24 is closed unless it had already been closed during shutting off of the oil burner. A short time later voltage is applied to the ignition electrodes 30 and the ; electro-magnetically operable valve 18 is subsequently opened so that oil supplied by the oil pump 10 reaches the pressure atomising nozzle 6. At the same time, air is supplied by means of the blast 14 to the chamber 4. The mixture produced is ignited by the ignition electrodes 30. A flame is thereby produced in that part of the flame tube 42 situated in front of the downstream end of the mixing tube 38. At the same time that ignition occurs, the throttle flap 24 is moved into the operating position under the control of control apparatus.
The diameter of the orifice 36 is such that the air inside the mixing tube 38 has a velocity such that drops of atomised oil do not form on the inner wall of the mixing tube 38 when the . . . '~ , . ' . . .
10~011~ ' air throttle flap is open. By means of the core stream of air, oxygen-poor combustion gas is sucked through the annular space around the mixing tube 38 and through the upstream end of the mixing tube 38 or through openings in the rear wall of the mixing tube at its upstream end. These hot combustion gases surround the core stream and give up heat thereto. An additional criterion for the dimension of the orifice 36 and the air velocity is that the air velocity in the mixing tube ! 38 should be greater than the velocity of propagation of the flame in order to ensure that the flame burns at a distance from the downstream end of the mixing tube 38. The stated operating conditions give the result that the distance between the end of the mixing tube 38 adjacent the wall 34 and said wall 34 is small as possible. This distance must be chosen in such a way that the recirculating gases flowing into the mixing tube 38 are as loss-free as possible and are able to mix with the oil cloud/air mixture of the core stream for the purpose of heat exchange. With experlmental burners the following dimensions have been found to be favourable:-1. Using a pressure atomising nozzle giving a throughput of 0.5 to 0.65 gal/hr and Diameter of the orifice D3 23.5-26 mm Internal diameter of the mixing tube Dl 35 mm Internal diameter of the flame-tube D2 76 mm a very stable blue flame was produced over the whole range of throughput.
. .
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- lOB0~12 2. Using a pressure atomising nozzle giving a throughput of 0.65 to 0.9 ga~/hr, the *bmeter D3 of the orifice 36 was increased to 25-31 mm with the remaining dimensions kept constant. Once again a stable blue flame was produced over the whole range of throughput.
A series of models developed for fabrication had the following principal dimensions (all meansurements in mm):-. .
Model Dl D2 D3 Ll L2~ L4 60Zle 1- gal/hr Li~
2 36 77 26 S7 225 9 0.65
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.
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the tube simultaneously through the orifice, partial combustion takes place with an excess of combustible material. These -combustion gases are returned and again enter the end of the mix-ing or vaporisation tube opposite the orifice plate at the same time as the spray of fuel. In this known burner the inner wall is provided with holes through which the greater part of the air of combustion enters in the form of a secondary air flow. (Proc.
World Petr. Congr., 7th Volume 7, Sect. on Application and New Uses, Part 1, p 119 f f ) . `
An oil burner with a blue f lame with recirculation is also known in which the orifice plate is situated in a tube which exte~ds so far in the upstream direction that the nozzle and the nozzle support are situated completely within the tube. With such a burner the flame should burn immediately behind the ori-f ice plate and part of the combustion gas should be recirculated through an annular space between the tube and an outer tube (ibid).
An oil burner is also known in which oil is sprayed directly into a tuhe which is surrounded by an outer recircula-tion tube connected to the inner tube by means of bores UIC Pat-ent F18213 issued on November 10th 1954 to Thermal Research and Engineering Company.
It is an object of the invention to design a blue-flame oil burner incorporated features of ,~r~nced conventional technology and which has a high operating reliability.
According to the invention there is provided an oil burner of the kindin which vaporised fuel is capab1e of burning with a blue flame and having provision for recirculation of part of the combustlon gases within a flame tube, the oil burner com-~,..~
- 10~0112 prising the flame tube, a wall extending transversely of the flame tube and defining the upstream end thereof, the wall having therein a metering orifice through which air enters the flame tube, the orifice being the only air inlet into the flame tube, an oil atomising device positioned upstream of the wall and arran- ~
ged to discharge an oil spray through the orifice into the flame :
tube, and a mixing tube positioned within the flame tube and ~
aligned with the orifice, the mixing tube having its upstream end ~.
spaced axially from the wall by a distance such that the periph-eral area of the space between the wall and the upstream end of the mxing tuhe and defined within an imaginary upstream extension :~
of the peripheral wall of the mixing tube to the transverse wall is between one and three times the difference in cross-sectional area between the upstream end of the mixing tube and the orifice, the mixing tube having a length, L,and a cross-sectional area at the upstream end thereof equal to the area of a circle having a `~
diameter, D, such that the ratio L/D is between 1.0 and 1.75, and the flame tube having an equivalent ratio L/D of between 2.0 and 5Ø
. Preferably the ratio L/D of the mixing tube is equal ; 20 to or is approximately 1.5.
Preferably also the ratio L/D of the flame tube is between 2.5 and 3Ø
In the preferred embodiment the cross-sectional area of the mixing tube is between 1.5 and 3.0 times the cross-sect-ional area of the orifice.
The flame tube and the mixing tube may have constant cross-section over their length. For example, the flame tube and the ~" .
, 10801~Z
mixing tube may both be designed to be cylindrical.
It may,of course, be convenient for silencing to design the flame tube wlth a cross-section of varylng orm, ~or ex~mple with a conLcal enlargement or even in a star shape.
A special problem with blue-flame oil burners ls the reliable ignition of the flame in the variable starting conditions which occur in practice, for example relighting a burner which is still hot. According to a feature of the invention the necessary reliability of ignition is achieved in that the burner is started with an air pressure below that of the full-load operation. The supply of air is then quickly increased after the opening of the oil valve to an air fraction sli~htly above the stoichiometric ratio with which the oil burner is then supplied.
Operation in the manner described is preferably achieved in that the air flap of the blower is provided with a drive and that time switch means are provided for operation of the drive.
For example, an electric or hydraulic motor may be provided as the drive which is preferably connected to the air flap through a self-locking gear mechanism.
It is also possible to use an electrically excited magnetic device or a hydraulic cylinder in each case with time-controlling damping members.
It may also be convenient when starting-up either in conjunction with or instead of throttling the air supply to the burner to operate with a throttled flow of oil mixture which can then be quickly brought up to the full air-oil mixture flow.
: , . : ~ , : , . . :
;
, -" : ~:': : .. , , ., ;
.: ~. :, ., lOflO11;2 By way of example an embodiment of the invention is illustrated in the accompanying drawing and is described in detail in the following with reference to the drawing, which shows a longitudinal section through an oil burner according to the invention together with its control and supply devices.
The burner 2 illustrated includes a chamber 4 in which a pressure atomising nozzle 6 is mounted in a known manner at the end of an oil supply pipe 8. Oil is fed into the pipe 8 by an oil pump 10 which is driven by a motor 12 which also drives a blower rotor 14 in a known manner. The pump 10 delivers oil through a hand-operated throttle valve 16 and an electromagnetically-operated shut-off valve 18 into the oil pipe 8 which carries the atomising nozzle 6. The blower 14 delivers air through a duct 20 into the housing 4 through a lS throttle valve 22 having air flap 24 whlch can be adjusted by a motor 26. A pair of ignition electrodes 30 is carried by a support 28 mounted on the oil pipe 8 and is connected to an ignition transformer 32.
At a distance L3 from the mouth of the pressure atomising nozzle 6 there i8 a wall 34 having a metering orifice 36 therein coaxial with the nozzle. At a distance from the orifice 36 there is a mixing tube 38 which is attached to the wall 34 by mounting rods 40. The mixing tube 38 is situated inside an outer tube 42 which forms the flame tube. In this example, the orifice 36, the mixing tube 38 and the flame-tube 4Z are circular but they need not be.
The diameter D3 of the orifice 36 and the arrangement and dimensions of the mixing tube 38 and of the flame-tube 42 are in a prdeter~ined critical relationship to each other which : ,. . ~ , :.
' '' '' : ~ :
` - 10801~
will be discussed in detail in the following.
The atomising nozzle 6 should be adjustable in the axial direction in order to vary the through-put of air and the oil cloud input and thus make it possible to achieve the optimum composition of the mixture.
The diameter D3 Of the orifice 36 should be chosen in such a way that at a delivery pressure of the blast 14 which corresponds to the delivery pressure normal in commercial oil ~;
burners, the air flow through the orifice 36 in the wall 34 has a predetermined velocity, the orifice being the only pas- - r sage for combustion air.
'l The diameter Dl of the mixing tube 38 is at least 1.25 and at maximum 1.7 and is preferably 1.4 to 1.45, times the diameter D3 of the orifice 36. Alternatively, the ratio of the cross-sectional area of the mixing tube and the orifice is between 1.5 and 3.0 where the mixing tube and/or the orifice are not of circular cross-section. The length Ll of the mixing tube is between 1.75 and l.ODl where Dl is the diameter of the mixing tube, and preferably Ll = 1.5Dl.
The distance L4 of the mixing tube 38 from the wall 34 is chosen in such a way that a flow cross-section, radially of the mixing tube 38, which is at least 1 to 3 times the differ-ence between the cross-sections of the orifice 36 and of the mixing tube 38 is produced between the upstream end of the mix-ing tube 38 and the wall 34. In other words, the peripheral area of the space between the wall 34 and the upstream end of the mixing tube 38 and defined within an imaginary upstream 10~0112 extension of the peripheral wall of the mixing tube 38 to the wall 34 is between one and three times the difference in cross-sectional area between the upstream end of the mixing tube 38 and the orifice 36. The diameter D2 of the flame tube 42 is approximately twice to 2.5 times the diameter Dl of the mixing tube and the ratio of the length L2 to the diameter D2 of the flame tube is between 2:1 and 5:1 and is preferably between 2.5:1 and 3:1.
A spray cone of approximately 60 to 80 degrees is convenient for the pressure atomising nozzle 6. Particularly good results were obtained with nozzles with hollow spray cones. When the oil burner is to be started, the motor 12 is first switched on inthe normal way. At the same time, the throttle flap 24 is closed unless it had already been closed during shutting off of the oil burner. A short time later voltage is applied to the ignition electrodes 30 and the ; electro-magnetically operable valve 18 is subsequently opened so that oil supplied by the oil pump 10 reaches the pressure atomising nozzle 6. At the same time, air is supplied by means of the blast 14 to the chamber 4. The mixture produced is ignited by the ignition electrodes 30. A flame is thereby produced in that part of the flame tube 42 situated in front of the downstream end of the mixing tube 38. At the same time that ignition occurs, the throttle flap 24 is moved into the operating position under the control of control apparatus.
The diameter of the orifice 36 is such that the air inside the mixing tube 38 has a velocity such that drops of atomised oil do not form on the inner wall of the mixing tube 38 when the . . . '~ , . ' . . .
10~011~ ' air throttle flap is open. By means of the core stream of air, oxygen-poor combustion gas is sucked through the annular space around the mixing tube 38 and through the upstream end of the mixing tube 38 or through openings in the rear wall of the mixing tube at its upstream end. These hot combustion gases surround the core stream and give up heat thereto. An additional criterion for the dimension of the orifice 36 and the air velocity is that the air velocity in the mixing tube ! 38 should be greater than the velocity of propagation of the flame in order to ensure that the flame burns at a distance from the downstream end of the mixing tube 38. The stated operating conditions give the result that the distance between the end of the mixing tube 38 adjacent the wall 34 and said wall 34 is small as possible. This distance must be chosen in such a way that the recirculating gases flowing into the mixing tube 38 are as loss-free as possible and are able to mix with the oil cloud/air mixture of the core stream for the purpose of heat exchange. With experlmental burners the following dimensions have been found to be favourable:-1. Using a pressure atomising nozzle giving a throughput of 0.5 to 0.65 gal/hr and Diameter of the orifice D3 23.5-26 mm Internal diameter of the mixing tube Dl 35 mm Internal diameter of the flame-tube D2 76 mm a very stable blue flame was produced over the whole range of throughput.
. .
. .
.. , . ,; . . . - .. .
' ' : : ' . `;, . :
.' :. :: ~ :: . .
- : - . :
~' ' , ' ' ; .
- lOB0~12 2. Using a pressure atomising nozzle giving a throughput of 0.65 to 0.9 ga~/hr, the *bmeter D3 of the orifice 36 was increased to 25-31 mm with the remaining dimensions kept constant. Once again a stable blue flame was produced over the whole range of throughput.
A series of models developed for fabrication had the following principal dimensions (all meansurements in mm):-. .
Model Dl D2 D3 Ll L2~ L4 60Zle 1- gal/hr Li~
2 36 77 26 S7 225 9 0.65
3 36 77 29 52 225 14 0.75 In all the models the distance L3 of the nozzle opening from the front face of the wall 34 was 2 mm.
Maintenance of the following combustion data was established for all ~odels on the test bench:-C2 = 155~ (approximate theoretical maximum) Soot = 0 CO = 0.01 -- ~0 --~ lOBOllZ
With blue flames, monitoring of the flame cannot be carried out optically. To guarantee a reliable automatic operation of the blue-burning flame monitoring is possible by means of an ; ionisation detector 44 which is connected in known manner to r a control device 46 by means of which, when tlie flame is extinguished, the supply of oil is cut off by closing the valve 18 and the motor 12 is switched off. After the flame has been produced the ignition device is also switched off by the control device in known manner.
It has been shown in practice that it is essential that the mixing tube 38 should be designed with as small a volume as possible, and thus, for given dimensions, with as small a wall thickness as possible. This ensures that the mixing tube 38 will glow bright red, so that a large portion of the heat of the recirculating combustion gases is transferred to the mixture of air and oil drops in the form of radiant heat, so that, once again, the complete vaporisation of the oil without droplets impinging on hot surfaces is ensured. With the aforesaid ratio Ll:Dl for the mixing tube it is ensured that the mixing tube is surrounded over its whole length by oxygen-poor combustion gases so that with mixing tubes of heat resistant steel it is not possible for any marked scaling or oxidation of the mixing tube to occur. The mixing tube may also be made from heat resistant ceramic material. The support of the mixing tube 38 can be effected, instead of by the axial arms 40, by radial arms which should then be mounted on the inside of the flame tube 42.
With stoichiometric combustion in the flame tube 42 . ~
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1080~12 practically no free oxygen is present. This is another reason why the flame tube 42 may be made of heat resistant steel without risk of wear due to scaling or oxidation.
A~ernatively, the flame tube 42 may be made from a heat resistant ceramic material or a steel tube having a heat resistant ceramic coating may be used. It is possible to arrange for the flame tube to be cooled, for example, the heating water. In this case the flame tube may, for example, form part of the heat exchange system of the boiler. With cooled flame tubes, it is not necessary to use hightly heat resistant materials.
Combustion in the oil burner described is to a large extent independent of the size and shape of the combustion chamber of the boiler. Under very unfavourable conditions, resonance phenomena may, however, occur during the ignition phase. These can be prevented by providing the wall of the flame tube 42 with a few holes in the region of the flame front. The development of noise may also be caused by a change in the flame cross-section. For example to reduce noi~e, a conlcal expansion of the flame-tube may be provided or the flame-tube, downsteeam of the flame zone, may be given a star-shaped cross-section.
A special problem with oil burners burning with a blue flame is that of guaranteeing reliable ignition under all working conditions. According to a feature of the invention, reliable ignition is achieved by, at the moment of ignition, supplying the burner with less than the stoichiometric air quantity required relative to the nominal load. For this '; , ~ ; ~ . , 1 1~8011Z
purpose the air flap 24 of the throttle valve 22 is moved to a suitable starting position by the adjusting motor so that on fresh ignition only, a suitably adjusted less than stoichiometric air quantity is supplied to the chamber 4. After the oil has ignited, the air flap 24 is moved by the adjusting motor 26 into the open position in which the quantity of air required for stoichiometric combustion is allowed to pass through the valve 22. The adjusting motor 26 may be switched on at the same time that the electro-magetically-operable valve 18 is opened, a finite time delay necessary being produced by means of a step-down gearing and, if necessary, accessory electrical control elements. This method of operation has the advantage that the air quantity is increased continuously. Switching on of the motor may also occur in dependence of the detection of a flame by means of the ionisation indicator 44. As the drive for the air flap, it would also be possible to provide an electro-magnetic device with known means of delay. A delay could be ensured for both an electro-magnetic device and an adjusting motor by means of a semi-conducting resistor. It has been established that, in general, in order to achieve reliable ignition, it is sufficient to start the burner with less than stoichiometric air quantity for a duration of about 3 to 5 seconds. It has been established that within this time, a stable recirculation flow is achieved with simultaneous heating of the mixing tube to the operating temperature. During starting with less than the stoichiometric air quantity, as described, no formation of soot was observed. Probably the .eason for this is that the amount of air present at any time within the combustion chamber - , -- :
OllZ
of the boiler is sufficient to ensure that the necessary oxygen for complete combustion is available. Depending on the conditions in the boiler at a particular time it may be necessary to increase the time allowed before the complete opening of the throttle flap occurs to 6 to lO seconds.
From a general point of view it is important for reliable ignition, to start the burner with an air velocity less than the air velocity at full load. Conveniently, it has been shown that during starting an excess pressure of 23 to 25 mm head of water during full air-fuel mixture flow.
If a hydraulically-operated adjusting motor is used, it is possible to employ the heating oil compressed by the pump 10 as the pressure fluid. Under certain circumstances it may also be convenient to provide ~ans by which it is possible to start the burner with, in addition to the throttling of the air stream, a throttled stream of oil as well. Then the stream of oil is raised to full flow in the same time period as that stated hereinbefore for the air stream. It is possible in this case, to keep the period of the less than stoichiometric operation short during starting and in the ideal case to maintain stoichiometric conditions of combustion even during starting the burner. It is, a necessary condition that even with a decreased flow of oil,the atomisation of the oil is not impaired. Up to a certain size, larger oil drops are acceptable since the walls, in particular the wall of the mixing tube, the temperature of which is essentially equal to the temperature of the boiler water (about 70-90C) during the starting process, have a cer~n storage capacity, that is to . . , ~ .
.
say larger drops of oil can settle on the walls at first and form an oil film there which will evaporate once full air-fuel mixture flow has been achieved.
In order to be able to operate the burner with maximum air-fuel mixture flow under varying conditions with as constant an excess of air as possible, that is as accurately stoichiometrically as possible, it is convenient to provide means by which it is possible to adjust the flow rates of air and/or oil automatically in response to momentary changes in operational conditions, in particular air pressure, air tempeature and/or the boilder draught.
Withp~essure atomising nozzles having a high throughput, the fine atomisation necessary for vaporisation is often no longer achievable. For burners of high power it may therefore be convenient to arrange a plurality (at least two) of nozzles at a distance from one another, either parallel or at an angle to each other, where the cross-section of the orifice 36 in the wall 34, the mixing tube 38 and, where necessary, the flame-tube 42 are geometrically adapted in a suitable manner.
The orifice 36 may, as illustrated, be a simple stamped-out opening in a disc-shaped wall 34. The orifice 36 may, however, be formed so as to project for a short distance in the form of a tube with an angular or a rounded-off transition to the wall 34.
, : ,. -
Maintenance of the following combustion data was established for all ~odels on the test bench:-C2 = 155~ (approximate theoretical maximum) Soot = 0 CO = 0.01 -- ~0 --~ lOBOllZ
With blue flames, monitoring of the flame cannot be carried out optically. To guarantee a reliable automatic operation of the blue-burning flame monitoring is possible by means of an ; ionisation detector 44 which is connected in known manner to r a control device 46 by means of which, when tlie flame is extinguished, the supply of oil is cut off by closing the valve 18 and the motor 12 is switched off. After the flame has been produced the ignition device is also switched off by the control device in known manner.
It has been shown in practice that it is essential that the mixing tube 38 should be designed with as small a volume as possible, and thus, for given dimensions, with as small a wall thickness as possible. This ensures that the mixing tube 38 will glow bright red, so that a large portion of the heat of the recirculating combustion gases is transferred to the mixture of air and oil drops in the form of radiant heat, so that, once again, the complete vaporisation of the oil without droplets impinging on hot surfaces is ensured. With the aforesaid ratio Ll:Dl for the mixing tube it is ensured that the mixing tube is surrounded over its whole length by oxygen-poor combustion gases so that with mixing tubes of heat resistant steel it is not possible for any marked scaling or oxidation of the mixing tube to occur. The mixing tube may also be made from heat resistant ceramic material. The support of the mixing tube 38 can be effected, instead of by the axial arms 40, by radial arms which should then be mounted on the inside of the flame tube 42.
With stoichiometric combustion in the flame tube 42 . ~
~. . - . . , -:: , : . , ,:: ~
1080~12 practically no free oxygen is present. This is another reason why the flame tube 42 may be made of heat resistant steel without risk of wear due to scaling or oxidation.
A~ernatively, the flame tube 42 may be made from a heat resistant ceramic material or a steel tube having a heat resistant ceramic coating may be used. It is possible to arrange for the flame tube to be cooled, for example, the heating water. In this case the flame tube may, for example, form part of the heat exchange system of the boiler. With cooled flame tubes, it is not necessary to use hightly heat resistant materials.
Combustion in the oil burner described is to a large extent independent of the size and shape of the combustion chamber of the boiler. Under very unfavourable conditions, resonance phenomena may, however, occur during the ignition phase. These can be prevented by providing the wall of the flame tube 42 with a few holes in the region of the flame front. The development of noise may also be caused by a change in the flame cross-section. For example to reduce noi~e, a conlcal expansion of the flame-tube may be provided or the flame-tube, downsteeam of the flame zone, may be given a star-shaped cross-section.
A special problem with oil burners burning with a blue flame is that of guaranteeing reliable ignition under all working conditions. According to a feature of the invention, reliable ignition is achieved by, at the moment of ignition, supplying the burner with less than the stoichiometric air quantity required relative to the nominal load. For this '; , ~ ; ~ . , 1 1~8011Z
purpose the air flap 24 of the throttle valve 22 is moved to a suitable starting position by the adjusting motor so that on fresh ignition only, a suitably adjusted less than stoichiometric air quantity is supplied to the chamber 4. After the oil has ignited, the air flap 24 is moved by the adjusting motor 26 into the open position in which the quantity of air required for stoichiometric combustion is allowed to pass through the valve 22. The adjusting motor 26 may be switched on at the same time that the electro-magetically-operable valve 18 is opened, a finite time delay necessary being produced by means of a step-down gearing and, if necessary, accessory electrical control elements. This method of operation has the advantage that the air quantity is increased continuously. Switching on of the motor may also occur in dependence of the detection of a flame by means of the ionisation indicator 44. As the drive for the air flap, it would also be possible to provide an electro-magnetic device with known means of delay. A delay could be ensured for both an electro-magnetic device and an adjusting motor by means of a semi-conducting resistor. It has been established that, in general, in order to achieve reliable ignition, it is sufficient to start the burner with less than stoichiometric air quantity for a duration of about 3 to 5 seconds. It has been established that within this time, a stable recirculation flow is achieved with simultaneous heating of the mixing tube to the operating temperature. During starting with less than the stoichiometric air quantity, as described, no formation of soot was observed. Probably the .eason for this is that the amount of air present at any time within the combustion chamber - , -- :
OllZ
of the boiler is sufficient to ensure that the necessary oxygen for complete combustion is available. Depending on the conditions in the boiler at a particular time it may be necessary to increase the time allowed before the complete opening of the throttle flap occurs to 6 to lO seconds.
From a general point of view it is important for reliable ignition, to start the burner with an air velocity less than the air velocity at full load. Conveniently, it has been shown that during starting an excess pressure of 23 to 25 mm head of water during full air-fuel mixture flow.
If a hydraulically-operated adjusting motor is used, it is possible to employ the heating oil compressed by the pump 10 as the pressure fluid. Under certain circumstances it may also be convenient to provide ~ans by which it is possible to start the burner with, in addition to the throttling of the air stream, a throttled stream of oil as well. Then the stream of oil is raised to full flow in the same time period as that stated hereinbefore for the air stream. It is possible in this case, to keep the period of the less than stoichiometric operation short during starting and in the ideal case to maintain stoichiometric conditions of combustion even during starting the burner. It is, a necessary condition that even with a decreased flow of oil,the atomisation of the oil is not impaired. Up to a certain size, larger oil drops are acceptable since the walls, in particular the wall of the mixing tube, the temperature of which is essentially equal to the temperature of the boiler water (about 70-90C) during the starting process, have a cer~n storage capacity, that is to . . , ~ .
.
say larger drops of oil can settle on the walls at first and form an oil film there which will evaporate once full air-fuel mixture flow has been achieved.
In order to be able to operate the burner with maximum air-fuel mixture flow under varying conditions with as constant an excess of air as possible, that is as accurately stoichiometrically as possible, it is convenient to provide means by which it is possible to adjust the flow rates of air and/or oil automatically in response to momentary changes in operational conditions, in particular air pressure, air tempeature and/or the boilder draught.
Withp~essure atomising nozzles having a high throughput, the fine atomisation necessary for vaporisation is often no longer achievable. For burners of high power it may therefore be convenient to arrange a plurality (at least two) of nozzles at a distance from one another, either parallel or at an angle to each other, where the cross-section of the orifice 36 in the wall 34, the mixing tube 38 and, where necessary, the flame-tube 42 are geometrically adapted in a suitable manner.
The orifice 36 may, as illustrated, be a simple stamped-out opening in a disc-shaped wall 34. The orifice 36 may, however, be formed so as to project for a short distance in the form of a tube with an angular or a rounded-off transition to the wall 34.
, : ,. -
Claims (21)
1. An oil burner of the kind in which vaporised fuel is capable of burning with a blue flame and having provision for recirculation of part of the combustion gases within a flame tube, the oil burner comprising a flame tube, a wall extending trans-versely of the flame tube and defining the upstream end thereof, the wall therein having a metering orifice through which air enters the flame tube, the orifice being the only air inlet into the flame tube, an oil atomising device positioned upstream of the wall to discharge an oil spray through the orifice into the flame tube, and a mixing tube positioned within the flame tube, and aligned with the orifice, the mixing tube having its upstream end spaced axially from the wall by a distance such that the peripheral area of the space between the wall and the upstream end of the mixing tube and defined within an imaginary upstream ex-tension of the peripheral wall of the mixing tube to the trans-verse wall is between one and three times the difference in cross-sectional area between the upstream end of the mixing tube and the orifice, the mixing tube having a length, L, and a cross-sectional area at the upstream end thereof equal to the area of a circle having a diameter, D, such that the ratio L/D is between 1.0 and 1.75, and the flame tube having an equivalent ratio L/D of between 2.0 and 5Ø
2. An oil burner as claimed in claim 1, in which the ratio L/D of the mixing tube is substantially 1.5.
3. An oil burner as claimed in claim 1, in which the ratio L/D of the flame tube is between 2.5 and 3Ø
4. An oil burner as claimed in claim 1, 2 or 3, in which the cross-sectional area of the mixing tube is between 1.5 and 3.0 times the cross-sectional area of the orifice where the mixing tube and/or the orifice are not of circular cross-section.
5. An oil burner as claimed in claim 1, 2 or 3, in which the distance between the atomising device and the trans-verse wall is substantially 2mm.
6. An oil burner as claimed in claim 1, 2 or 3, in which the flame tube has a substantially constant cross-section throughout its length.
7. An oil burner as claimed in claim 1, 2 or 3, in which the flame tube and the mixing tube are each cylindrical.
8. An oil burner as claimed in claim 1, 2 or 3, in which the flame tube has a profile producing a varying cross-section, at least downstream of the flame zone.
9. An oil burner as claimed in claim 1, 2 or 3, in which the mixing tube has a cross-sectional area varying along its length.
10. An oil burner as claimed in claim 1, in which the air to the upstream side of the transverse wall is supplied by a throttle valve, said throttle valve including an air flap movable to an open position, driving means therefore and time switch means controlling the operation of said driving means.
11. An oil burner as claim in claim 10, in which the driving means for the air flap is a motor including a self-locking gear mechanism by which said motor automatically engages the air flap.
12. An oil burner as claim in claim 1,including control means to control the rate of flow of at least one of the air flow and the oil flow, said control means being dependent upon a para-meter selected from the group comprising:- air pressure, air temperature and burner draught.
13. An oil burner as claimed in claim 1, 2 or 3, in which the flame-tube is water-cooled.
14. An oil burner as claimed in claim 1, 2 or 3, in which the flame tube is a standard element of a boiler.
15. An oil burner as claimed in claim 1, 2 or 3, in which the oil atomising device is an oil spray nozzle of the kind operable with a hollow spray cone.
16. An oil burner as claimed in claim 1 including control means whereby the burner is started with a low air pres-sure compared with that corresponding to full air-fuel mixture flow.
17. An oil burner as claimed in claim 16, including control means whereby the burner is started with a smaller rate of flow of air compared to that corresponding to full air-fuel mixture flow.
18. An oil burner as claimed in claim 10, including control means by which the burner is started with the air flap in a partly-closed position and the supply of air is increased after the opening of an oil supply valve by the continuous open-ing of the air flap until the quantity of air supply is slightly greater than the stoichiometric value.
19. An oil burner as claimed in claim 1, 2 or 3, including control means whereby the burner is started with the rate of supply of oil reduced compared with that at full air-fuel mixture flow.
20. An oil burner as claimed in claim 1, 2 or 3, wherein said flame tube and mixing tube are circular in cross-section and wherein the internal diameter of said flame tube is approximately 2 to 2.5 times the internal diameter of said mixing tube.
21. An oil burner as claimed in claim 10, 11 or 12, wherein said flame tube and mixing tube are circular in cross-section and wherein the internal diameter of said flame tube is approximately 2 to 2.5 times the internal diameter of said mixing tube.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2700671A DE2700671C2 (en) | 1977-01-08 | 1977-01-08 | Blue-burning oil burner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1080112A true CA1080112A (en) | 1980-06-24 |
Family
ID=5998348
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA292,449A Expired CA1080112A (en) | 1977-01-08 | 1977-12-06 | Blue-flame oil burner |
Country Status (20)
| Country | Link |
|---|---|
| JP (1) | JPS5388233A (en) |
| AT (1) | AT383203B (en) |
| AU (1) | AU511042B2 (en) |
| BE (1) | BE862558A (en) |
| CA (1) | CA1080112A (en) |
| CH (1) | CH628724A5 (en) |
| DE (1) | DE2700671C2 (en) |
| DK (1) | DK146664C (en) |
| ES (1) | ES465796A1 (en) |
| FI (1) | FI59861C (en) |
| FR (1) | FR2377002A1 (en) |
| GB (1) | GB1592490A (en) |
| GR (1) | GR64693B (en) |
| IE (1) | IE46538B1 (en) |
| IT (1) | IT1088397B (en) |
| LU (1) | LU78704A1 (en) |
| NL (1) | NL176705C (en) |
| NO (1) | NO145998C (en) |
| SE (1) | SE429473B (en) |
| YU (1) | YU39258B (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2918416C2 (en) * | 1979-05-08 | 1985-05-15 | Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln | Gasification oil burner |
| DE2922083C2 (en) * | 1979-05-31 | 1984-02-09 | Hoch-Temperatur-Technik Gmbh, 4900 Herford | Flame tube for a burner-fired furnace |
| DE3007436C2 (en) * | 1980-02-28 | 1982-11-18 | Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln | Blue burner |
| DE3035707A1 (en) * | 1980-09-22 | 1982-04-08 | Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln | OIL AND GAS BURNERS FOR INSTALLATION IN HEATING AND STEAM GENERATING BOILERS |
| JPS58200911A (en) * | 1982-05-17 | 1983-11-22 | Inax Corp | Combustion method for liquid fuel and device therefor |
| DE3241730A1 (en) * | 1982-11-11 | 1984-05-17 | Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn | GASIFICATION OIL BURNER WITH AN OIL SPRAYING DEVICE |
| DE3243398C2 (en) * | 1982-11-24 | 1985-03-28 | Danfoss A/S, Nordborg | Evaporation burners for liquid fuel |
| DE3304214A1 (en) * | 1983-02-08 | 1984-04-26 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg | BURNER FOR INSTALLATION IN HEATING AND STEAM GENERATING SYSTEMS |
| DE3430010A1 (en) * | 1984-08-16 | 1986-02-27 | Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn | BURNER FOR HOT GAS GENERATION |
| EP0232677B1 (en) * | 1985-12-30 | 1989-08-09 | VTH AG Verfahrenstechnik für Heizung | Burner, particularly burner for burning liquid fuel in gaseous state |
| ES2021465B3 (en) * | 1987-03-13 | 1991-11-01 | Fuellemann Patent Ag | BURNER |
| DE3731846C1 (en) * | 1987-09-22 | 1989-04-27 | Abig Werke Carry Gross Gmbh | Burner for fluid, fossil, carbonaceous fuel |
| US5015173A (en) * | 1988-06-09 | 1991-05-14 | Vth Ag Verfahrenstechnik Fur Heizung | Burner for the combustion of liquids in the gaseous state |
| DE3906854C1 (en) * | 1989-03-03 | 1990-10-31 | Buderus Heiztechnik Gmbh, 6330 Wetzlar, De | Burner tube for a blue-burning oil burner |
| DE4009222A1 (en) * | 1989-07-13 | 1991-01-24 | Elco Oel & Gasbrenner | BURNER FOR STOECHIOMETRIC COMBUSTION OF LIQUID OR GASEOUS FUELS |
| DE3928214A1 (en) * | 1989-08-25 | 1990-03-08 | Zimmermann Hans Georg Dipl Ing | BURNER WITH FUEL GAS RECIRCULATION FOR FLOWABLE FUELS |
| DE4113412C2 (en) * | 1991-04-20 | 1999-04-01 | Saacke Gmbh & Co Kg | Device for burning liquid or gaseous fuel for a furnace |
| DE4230778C2 (en) * | 1992-09-15 | 1997-03-20 | Man B & W Diesel Ag | Flame tube for a burner for burning a liquid or gaseous fuel |
| DE4430888A1 (en) | 1993-12-18 | 1995-07-06 | Deutsche Forsch Luft Raumfahrt | Adjustable blue burner |
| DE4415676C2 (en) * | 1994-05-04 | 2001-03-01 | Man B & W Diesel Ag | burner |
| DE102010063524A1 (en) | 2010-12-20 | 2012-06-21 | Bodo Wyrwa | Adjustable burner for combustion of heating oil at oil heating system for building, has injector openings manually or electronically controllable, continuously releasable or closable by annular control element with slot like openings |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH327648A (en) * | 1953-11-06 | 1958-02-15 | Thermal Research & Engineering | Process for achieving combustion with high heat generation |
| DE1177271B (en) * | 1955-01-11 | 1964-09-03 | Thermal Res & Engineering Corp | Liquid fuel burner |
| DE1258007B (en) * | 1956-02-04 | 1968-01-04 | Eugen Klein Dipl Ing | Burners for flowing fuels |
| DE1220544B (en) * | 1957-09-09 | 1966-07-07 | Robert Von Linde Dipl Ing | Burners for flowing fuels |
| DE1064188B (en) * | 1958-08-16 | 1959-08-27 | Willi Broedlin | Process for the combustion of liquid hydrocarbons, in particular heating oil |
| DE1401127A1 (en) * | 1958-08-16 | 1968-12-12 | Willi Broedlin | Method and device for blue-brand operation of atomizing oil burners |
| DE1266433B (en) * | 1962-10-26 | 1968-04-18 | Optimal Oelfeuerungsmaschb G M | Oil gasification burner |
| CH408262A (en) * | 1964-02-26 | 1966-02-28 | Elco Oelbrennerwerk Ag | Method for starting an oil burner and pressure regulating device for carrying out this method |
| US3316955A (en) * | 1965-03-08 | 1967-05-02 | Master Cons Inc | Oil burner apparatus |
| US3294146A (en) * | 1965-04-15 | 1966-12-27 | Coen Company | Metered combustion air supply system |
| CH469234A (en) * | 1967-01-12 | 1969-02-28 | Ygnis Sa | Process for burning, in particular, liquid or gaseous fuels and heating boilers for carrying out the process |
| NL6912988A (en) * | 1969-08-26 | 1971-03-02 | ||
| DE2059693A1 (en) * | 1970-12-04 | 1972-06-15 | Werner Pieper | Liquid fuel burners |
| DE2248348C3 (en) * | 1972-10-02 | 1975-06-12 | Wamsler Herd- Und Ofen Gmbh, 8000 Muenchen | Oil heater with evaporation burner |
-
1977
- 1977-01-08 DE DE2700671A patent/DE2700671C2/en not_active Expired
- 1977-11-14 AT AT0813477A patent/AT383203B/en not_active IP Right Cessation
- 1977-11-18 SE SE7713044A patent/SE429473B/en not_active IP Right Cessation
- 1977-11-22 CH CH1427277A patent/CH628724A5/en not_active IP Right Cessation
- 1977-11-23 FI FI773541A patent/FI59861C/en not_active IP Right Cessation
- 1977-11-23 NO NO774006A patent/NO145998C/en unknown
- 1977-12-05 GB GB50523/77A patent/GB1592490A/en not_active Expired
- 1977-12-06 IE IE2479/77A patent/IE46538B1/en not_active IP Right Cessation
- 1977-12-06 CA CA292,449A patent/CA1080112A/en not_active Expired
- 1977-12-07 DK DK543577A patent/DK146664C/en not_active IP Right Cessation
- 1977-12-14 NL NLAANVRAGE7713861,A patent/NL176705C/en not_active IP Right Cessation
- 1977-12-15 IT IT30770/77A patent/IT1088397B/en active
- 1977-12-16 LU LU78704A patent/LU78704A1/xx unknown
- 1977-12-27 YU YU3091/77A patent/YU39258B/en unknown
- 1977-12-28 JP JP15862077A patent/JPS5388233A/en active Granted
- 1977-12-29 AU AU32057/77A patent/AU511042B2/en not_active Expired
- 1977-12-30 BE BE184041A patent/BE862558A/en not_active IP Right Cessation
-
1978
- 1978-01-04 FR FR7800178A patent/FR2377002A1/en active Granted
- 1978-01-05 ES ES465796A patent/ES465796A1/en not_active Expired
- 1978-01-07 GR GR55111A patent/GR64693B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| IE772479L (en) | 1978-07-08 |
| AU511042B2 (en) | 1980-07-24 |
| SE429473B (en) | 1983-09-05 |
| DE2700671C2 (en) | 1988-07-28 |
| SE7713044L (en) | 1978-07-09 |
| NL176705C (en) | 1985-05-17 |
| FR2377002B1 (en) | 1983-04-29 |
| ATA813477A (en) | 1986-10-15 |
| DK146664C (en) | 1984-05-07 |
| NL7713861A (en) | 1978-07-11 |
| DE2700671A1 (en) | 1978-07-20 |
| GB1592490A (en) | 1981-07-08 |
| FI59861C (en) | 1981-10-12 |
| DK543577A (en) | 1979-07-09 |
| FR2377002A1 (en) | 1978-08-04 |
| AU3205777A (en) | 1979-07-05 |
| NL176705B (en) | 1984-12-17 |
| YU309177A (en) | 1982-08-31 |
| JPS5388233A (en) | 1978-08-03 |
| NO774006L (en) | 1978-07-11 |
| IT1088397B (en) | 1985-06-10 |
| IE46538B1 (en) | 1983-07-13 |
| ES465796A1 (en) | 1978-09-16 |
| NO145998C (en) | 1982-07-07 |
| AT383203B (en) | 1987-06-10 |
| YU39258B (en) | 1984-10-31 |
| DK146664B (en) | 1983-11-28 |
| LU78704A1 (en) | 1978-04-17 |
| GR64693B (en) | 1980-05-14 |
| JPS5732289B2 (en) | 1982-07-09 |
| CH628724A5 (en) | 1982-03-15 |
| FI773541A (en) | 1978-07-09 |
| NO145998B (en) | 1982-03-29 |
| FI59861B (en) | 1981-06-30 |
| BE862558A (en) | 1978-04-14 |
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