EP0122454B1 - Brûleur à huile de petite capacité - Google Patents

Brûleur à huile de petite capacité Download PDF

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Publication number
EP0122454B1
EP0122454B1 EP84102707A EP84102707A EP0122454B1 EP 0122454 B1 EP0122454 B1 EP 0122454B1 EP 84102707 A EP84102707 A EP 84102707A EP 84102707 A EP84102707 A EP 84102707A EP 0122454 B1 EP0122454 B1 EP 0122454B1
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EP
European Patent Office
Prior art keywords
nozzle
oil
light duty
bellows
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
Application number
EP84102707A
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German (de)
English (en)
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EP0122454A1 (fr
Inventor
Franklin Schmidt
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Individual
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Individual
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Publication date
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Priority to AT84102707T priority Critical patent/ATE41500T1/de
Publication of EP0122454A1 publication Critical patent/EP0122454A1/fr
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Publication of EP0122454B1 publication Critical patent/EP0122454B1/fr
Expired legal-status Critical Current

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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
    • F23D11/24—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
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/008—Flow control devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/027—Regulating fuel supply conjointly with air supply using mechanical means

Definitions

  • the invention relates to a small oil burner, the type specified in the first part of claim 1.
  • a small oil burner of this type is known from US-A 2 491 201.
  • the intake port of an air blower can be more or less shut off by means of a flap which can be actuated by a pivoting lever which can be adjusted by means of a cylinder-piston unit arranged outside the intake port and forming the actuator.
  • the air regulation apparently takes place in the area in front of the pump. The consequence of this is that a comparatively low dynamic pressure is present in the area behind the pump, so that changes in the draft in the chimney or pressure surges when starting up, etc., can have a relatively strong impact. This can lead to insufficient stability of the air flow in the area of the mixing zone, particularly when conveying smaller amounts of air.
  • the external arrangement of the actuator results in a very space-consuming construction, which is also from the conception of common, d. H. uncontrolled burner, deviates, so that difficulties are to be feared in case of retrofitting.
  • a very particular disadvantage of the known arrangement can also be seen in the structure of the mode of operation of the air setting itself.
  • the cylinder-piston unit provided to form the actuator can be acted upon by oil through a branch line branching from a pressure line leading to the injection nozzle.
  • this exposure is not such that a corresponding with the oil pressure, i. H. proportional adjustment of the piston of the cylinder-piston unit and thus a corresponding adjustment of the air by the oil pressure or vice versa.
  • the aforementioned stub leads through a solenoid valve, by means of which the stub can only be opened or closed, but the air line is also not opened or closed analogously to this. If the spur line is blocked by the solenoid valve, there is no oil on the cylinder-piston unit.
  • the piston of this unit is held in a first stop position by a spring, which corresponds to a first operating point. According to column 4, lines 20-25, the operating point corresponding to a full-load operation is set when the stub line is depressurized. To set a second operating point, the spur line is opened by the solenoid valve, so that pressure oil is present at the actuator forming the cylinder-piston unit.
  • this second operating point corresponds to a partial load operation. More than two operating points cannot be set at all in the known arrangement. There is no proportionality of any kind between the oil pressure at the actuator and the current air volume associated with it. Apart from this, solenoid valves of the type provided in the arrangement according to US Pat. No. 2,491,201 to shut off the spur line are comparatively susceptible to malfunctions, which can easily jam and thus lead to malfunctions. This risk is further increased in the known arrangement in that a similar solenoid valve is also arranged in the area of an oil return line, by means of which the return line can be opened or closed to set two operating points.
  • a bellows as the actuating device assigned to the actuator advantageously enables an arrangement which is concentric with the nozzle axis, which very much complies with the desired compact design.
  • a bellows is a very robust, fail-safe component that can be enlarged either by applying pressure from the outside or by expanding its contents, and vice versa, which enables both temperature-dependent and pressure-dependent activation. This is particularly advantageous with regard to a particularly sensitive adjustment of the respective air throughput to the respective oil throughput, since the oil throughput can be changed both by influencing the oil pressure and by influencing the oil temperature.
  • a very special advantage of the erfin Measures according to the invention can also be seen in the fact that not only two operating points can be set, but that practically an entire operating range can be traversed, whereby there is always a fixed dependence on oil and air throughput. This results in optimal operating conditions in the entire partial load range as well as in the full load range.
  • US Pat. No. 2,156,405 does indeed show an oil burner in which a throttle point formed by a constriction and a diaphragm interacting therewith is provided in the flow path of the combustion air in the area behind the fan.
  • the aperture must be adjusted by hand.
  • FR-A 23 60 044 contains the teaching that the oil throughput through the injection nozzle can be changed not only by influencing the pressure but also by influencing the temperature. A corresponding tracking of the air flow does not take place.
  • the oil burner 2 shown in FIG. 1, flanged in a known manner to a heat exchanger 1, for example in the form of a boiler, has a nozzle head 3 with an outer combustion air pipe 4 and a centrally arranged nozzle assembly 6, on which a nozzle holder 8 receiving an injection nozzle 7 is stored.
  • the burner tube 4 and the nozzle holder delimit an annular combustion air channel 5.
  • the injection nozzle 7 is designed as a swirl or simplex nozzle with a constant bore cross section and without oil return.
  • the injection nozzle 7 is supplied via a pressure connection 9, which is connected to a pump, not shown here, with heating oil having pump pressure, which is injected into the combustion chamber of the heat exchanger 1. This is supposed to be a combustion system used in private areas, for example.
  • the oil burner 2 is therefore designed for an hourly consumption below 5 kg.
  • a baffle plate 10 is provided which is known per se and has radial air passage slots and is simply attached to the nozzle holder 8 here.
  • Primary air reaches the combustion zone via the radial slots of the baffle plate 10.
  • Secondary air enters the combustion zone via an annular gap 11 between the baffle plate and the front, inwardly protruding end of the burner tube 4.
  • the ignition of the fuel-air mixture takes place via an ignition electrode 65 assigned to the injection nozzle 7.
  • a photo cell 66 is provided which scans the combustion zone and is arranged here in the area of the combustion air duct 5.
  • the amount of oil injected is permanently adapted to the energy requirement of the heat exchanger 1.
  • the combustion air supplied is adapted to the current oil throughput in such a way that essentially stoichiometric combustion is ensured.
  • the rate of temperature rise in the area of the heat exchanger 1 is detected and used as a control variable.
  • the control of the oil and air throughput that is to say the control of the energy supply to the heat exchanger 1, is carried out in such a way that the rate of temperature rise is, if possible, 0 or moves towards 0, which achieves a steady state between the energy supply and the energy output.
  • the outside temperature can be applied to the control variable as a level specification in the form of a cascade.
  • the air throughput through the combustion air duct 5 is controlled by changing its free flow cross section as a function of the load.
  • a throttle point 12 is provided, which is formed by a disk-shaped diaphragm 13 and a constriction 14 of the burner tube 4 cooperating therewith.
  • the throttle point 12 can be set in a manner specified in more detail below.
  • the oil throughput through the non-adjustable, non-returnable injection nozzle 7 is controlled by load-dependent influencing of the temperature and the pressure of the oil present on the inlet side at the injection nozzle 7.
  • the viscosity of heating oil decreases with increasing temperature.
  • the oil throughput can therefore be throttled by increasing the temperature and lowering the pressure and vice versa.
  • a heating device 15 is provided here, which is formed by a centrally arranged heating rod, on which the flow path of the heating oil supplied via the pressure connection 9 of the injection nozzle 7 in the form of a non-return, transverse cut annular channel 16 passes.
  • the heating device 15 can be controlled via signal lines 17 in dependence on the rate of temperature rise in the area of the heat exchanger 1 in such a way that the temperature is increased when less energy is required and vice versa.
  • the vehicle is started with a minimal oil throughput. This can be achieved in a simple manner by monitoring the temperature of the oil with the aid of a start-up thermostat 67, which only releases the burner operation when the required oil temperature has been reached.
  • a throttle point 18 is provided in the region of the flow path formed by the channel 16, the sealing surfaces 19 and 20 of which have to be lifted from each other against the force of a closing spring 21 by the oil passing through the throttle point.
  • the oil temperature which can be generated by means of the heating device 15 serves at the same time as a guide variable for setting a desired oil pressure and an air flow rate associated with the oil flow rate which is dependent on the oil temperature and the oil pressure.
  • the nozzle holder 8 is slidably mounted on the stationary nozzle assembly 6 in the illustrated embodiment.
  • the displaceable nozzle holder 8 practically forms a displaceable actuator for adjusting the diaphragm 13 fastened thereon and the closing spring 21 which exerts the closing force effective in the region of the throttle point 18 and can also be taken from it on one side.
  • a pressure chamber 23 is provided for displacing the displaceably mounted nozzle holder 8 against the force of a return spring 22 supported on the stationary nozzle assembly, here in the form of the interior of a cylindrical double bellows 24 surrounding the heating device 15, which through opposite surfaces of the stationary nozzle assembly 6 or one flange 25 fixed thereon and the nozzle holder 8, which is displaceably mounted in relation thereto, is limited.
  • the pressure chamber 23 is filled with a refrigerant that expands when heated and vice versa.
  • a heating device which can be activated in a load-dependent manner can be provided.
  • the heat transfer to the double bellows 24 takes place through the heating oil, which in turn can be tempered by means of the associated heating device 15.
  • the flow path of the heating oil formed by the channel 16 simply passes between the heating device 15 and the double bellows 24.
  • a reciprocable tube 26 is provided on the heating element forming the heating element 15, which is provided with a collar having the sealing surface 20, which engages behind an undercut edge forming the sealing surface 19 of the displaceable nozzle holder 6 and is supported on the nozzle end side by means of the closing spring 21.
  • the tube 26 is provided with a collar engaging behind the flange 25, on which the closing spring 21 engages, which can thus be taken along by the displaceable nozzle holder 8 forming an actuator.
  • the annular gap between the tube 26 and the heating device comprised by it is sealed.
  • the pipe 26, which is made of thermally conductive material is in contact with the thermally conductive contact on the outer heating surfaces of the heating device 15.
  • the flow path of the oil formed by the channel 16 leads radially outside the tube 26 between the tube and the double bellows 24.
  • the downstream throttling point 18 ensures that the entire space between the tube 26 and the double bellows 24 is filled with oil, so that reliable heat transfer to the double bellows 24 is ensured.
  • the energy supply to the heating device 15 takes place inversely proportional to the temperature rise speed in the area of the heat exchanger 1. If the temperature rise speed is too high and is to be reduced, the energy supply to the heating device 15 is increased, thus increasing the heat emission to the oil flowing through the channel 16, which increases leads to a reduction in the viscosity of the oil, which already leads to a reduction in the oil throughput when the oil pressure is constant at the injection nozzle 7 having a constant nozzle bore diameter.
  • the supply of energy to the heating device 15 accordingly leads not only to a reduction in the oil viscosity, but also to a lowering of the oil pressure effective for the injection and to a throttling of the air throughput adapted to the strongly throttled oil throughput, this being particularly noticeable in the secondary air area.
  • the tube 26 is provided with an extension 27 adjoining the collar having the sealing surface 20, which includes an annular gap 28 adjoining the throttle point 18 with the nozzle holder 8.
  • the oil reaches a comparatively high speed before it enters the threaded feed channel for the nozzle bore of the injection nozzle 7, which is designed as a swirl or simplex nozzle, via an upstream filter or sieve 29. Due to the high speed of the oil in the area of the annular gap 28, air pockets are entrained by the oil, so that no larger air bubbles can form.
  • a further oil filter 29a which is arranged in the region of the outlet cross section of the pressure connection 9, can be provided to increase operational reliability. Pre-filtering of the oil can be achieved in this way, so that no operational disturbances are to be feared even in the case of small gap widths of the order of 1/10 mm in the region of the throttle point 18.
  • the basic structure of the arrangement according to FIG. 2 corresponds to the arrangement described above.
  • the same reference numerals are therefore used for the same parts.
  • the double bellows 24 enclosing the pressure chamber 23 is delimited on the one hand by the nozzle holder 8 and on the other hand by a displaceable ring 30.
  • the nozzle holder 8 is immovably attached to the stationary nozzle assembly 6 by means of a shirt-like attachment or an opened sleeve 68 or the like.
  • the ring 30 in this case forms the displaceable actuator which serves to set a throttle point 12 provided in the region of the flow path of the air, formed by a constriction 14 and a displaceable diaphragm 13 associated therewith, and a throttle point 18 provided in the region of the flow path of the oil.
  • the combustion air channel delimited by the burner tube 4 is through an air guide tube 69 which comprises the nozzle block 6 and the nozzle holder 8 with a radial spacing, into a primary air channel 5a assigned to the radial slots of the baffle plate 10 and one between the annular gap 11 Baffle plate 10 and burner tube 4 assigned secondary air duct 5b divided.
  • the air guide tube 69 is arranged so that the air flow can be divided in the region of the constriction 14.
  • the metering of the air to be accomplished by the ring 30 forming the actuator takes place here by blocking the secondary air duct 5b.
  • the air guide tube 69 is firmly connected to the ring 30 and is provided in the region of its outer circumference with the diaphragm 13 assigned to the constriction 14.
  • the entrance to the primary air duct 5a remains unaffected by the orifice 13, which, even with a low total air throughput, results in a high proportion of primary air and thus ensures good nebulization.
  • the annular gap 11 between the baffle plate 10 and the burner tube 4 need not be changed in this embodiment.
  • the baffle plate 10 can therefore be arranged stationary.
  • the baffle plate 10 is fixed on the burner tube 4.
  • the air guide tube 69 is here up to the baffle plate 10. To accomplish the required mobility of the air guide tube 69, this is simply designed as a two-part telescopic tube. It would also be conceivable to accommodate the baffle plate 10 on the front end of the air guide tube 69 so that it could be formed in one piece and at the same time there would be an adjustability of the gap 11 between the baffle plate 10 and the burner tube 4.
  • the sleeve 68 connecting the nozzle assembly 6 to the nozzle holder 8 is simply provided with slots 31 in the adjustment region of the ring 30, through which holders 32 fastened on the ring 30 extend, to which the air guide tube 69 is fastened.
  • the ring 30 is supported by a return spring in the form of a single bellows 33 against the action of the pressure chamber 23 on the nozzle assembly 6.
  • the single bellows 33 seals the flow path of the oil in the form of the channel 16 surrounding the rod-shaped heating device 15, which is fed from the pressure connection 9 and is therefore under pump pressure, which also acts on the ring 30, so that no oil can escape through the slots 31.
  • the oil flow path formed by the channel 16 leads here between the rod-shaped heating device 15 and the pipe 26 surrounding it here with radial play, which is provided with a collar engaging behind the nozzle-side end face of the heating device 15 to form the throttle point 18.
  • the opposite end of the tube 16 engages behind the ring 30 and is supported thereon by means of the closing spring 21.
  • the space between the tube 26 and the double bellows 24 having a refrigerant charge is accessible from the flow path of the oil and is therefore filled with oil.
  • the front end of the tube 26 is located sealing against the wall of an associated bore of the nozzle holder 8, so that the entire oil throughput must pass through the throttle point 18.
  • the standing oil filling between pipe 26 and double bellows 24 ensures reliable heat conduction.
  • the force-based design is based on a given pump pressure so that the force caused by the standstill pressure within the pressure chamber 23, acting on the ring 30, is greater than the force of the closing spring 21, so that the actuator is not in a standstill position the full load is in a position corresponding to the minimum load, which can reduce the number of required movements of the bellows 24 and the bellows 33 and at the same time ensures that the sealing surface of the movable tube 26 suddenly closes the throttle point 18 in the manner of a quick-closing valve when the pump pressure is lost , which reliably prevents re-injection.
  • this also applies to the other embodiments.
  • an energy supply to the heating device 15 not only leads to a reduction in the viscosity of the oil, but at the same time also to a lowering of the pressure of the oil present at the injection nozzle 7 and at the same time to a throttling of the air throughput.
  • FIG. 7 The basic structure of the arrangement according to FIG. 7 corresponds to the above-described arrangement according to FIG. 2. The following description of FIG. 7 is therefore essentially limited to the differences, the same reference numerals being used for the same parts.
  • the double bellows 24, which on the one hand rests against the ring 30 forming an actuator and delimits the pressure chamber 23, is in direct contact with the stationary nozzle assembly 6.
  • the area between the ring 30 forming an actuator and the nozzle holder 8, which is fixedly connected to the nozzle block 6 via the sleeve 68, is sealed by the single bellows 33, which also acts as a return spring for the ring 30.
  • the arrangement of the double bellows 24 delimiting the pressure chamber 23 that is realized here advantageously leads to comparatively small actuating forces and thus to comparatively small bellows diameters and overall to a compact design.
  • the heating element forming the heating device 15 acts much warmer in its front area near the nozzle holder than in its rear area near the nozzle stock.
  • the refrigerant enclosed in the pressure chamber 23 is therefore advantageously only exposed to the lower temperatures to be expected in the rear area of the heating element.
  • Another advantage is that the refrigerant can be easily filled into the pressure chamber 23.
  • the nozzle assembly 6 is simply provided with an axial bore 71, which can be closed by means of a grub screw 72.
  • a thermal element 73 for sensing the temperature in the pressure chamber 23 can also advantageously be accommodated in the axial bore 71.
  • the arrangement of the thermocouple 73 on the nozzle side advantageously enables simple laying of the connections.
  • Monitoring the temperature of the pressure chamber 23 facilitates the control of the fuel throughput. This is regulated here in order to achieve a comparatively short controlled system as a function of the temperature in the pressure chamber 23, the rate of temperature rise in the area of the heat exchanger 1 being applied in the form of a cascade.
  • the throttle point 18 is delimited here by a disk 74 inserted into the nozzle holder 8, which is fixedly connected to the stationary nozzle assembly 6, and provided with a central bore, and a ball 75 arranged at the opposite end of the heating element forming the heating device 15.
  • the disk 74 having the bore 76 is stationary against a stop 77 formed by a shoulder etc. of the nozzle holder 8.
  • the heating element forming the heating device 15 is not firmly connected to the nozzle assembly 6 here, but rather is arranged so as to be movable in the axial and radial directions. In the axial direction, the heating element is supported on the ring 30 forming an actuator via the closing spring 21 which cooperates with it, which enables the throttle point 18 to be opened and closed.
  • the heating element In the radial direction, the heating element has so much play that the ball 75 can center itself on the facing edge of the bore 76.
  • the floating arrangement of the heating element forming the heating device 15 provided here therefore results in a reliable sealing seat in the region of the throttle point 18, without high accuracy being required when machining the heating element, which has an advantageous effect on the production outlay. Because of the stationary arrangement of the disk 74, a reliable sealing of the disk 74 with respect to the nozzle holder 8 can also be achieved with comparatively simple means.
  • a sleeve 79 which is supported by the single bellows 33 and is supported on the disk 74 inserted in the nozzle holder 8, is provided. This therefore specifies the strongest compression of the closing spring 21 and thus the highest closing force in the area of the throttle point 18.
  • a sleeve 80 screwed onto the heating element is provided to form a contact shoulder on the heating rod side and associated with the closing spring 21.
  • the heating element is provided with a threaded pin 81 placed on its front end, onto which the sleeve 80 can be screwed and which receives the ball 75 in the region of its front end.
  • the sleeve 80 which can be screwed onto the heating element is easily removable, so that parts located behind the sleeve, for example the closing spring 21, can be easily replaced. are possible.
  • the measures described above therefore also result in a high degree of ease of installation.
  • the sleeve 80 can be provided with threads 82 in the area of its outer circumference.
  • a guide tube 83 comprising the heating rod with radial play is provided, which is fastened to the ring 30 forming the actuator.
  • the guide tube is provided with a claw encompassing the edge of the ring 30 on the closing spring side, which is thus pressed against the shoulder of the ring 30 assigned to it by the closing spring 21. This ensures that the tube 23 is carried along with each movement of the ring 30.
  • the guide tube 83 results in a high flow rate of the oil and thus good heat transfer.
  • the guide tube 23 also provides a radial inner support for the double bellows 24, which ensures a high degree of kink resistance.
  • the displaceable nozzle holder 8 which here in turn represents the actuator for simultaneously influencing the air throughput and the oil pressure, can be displaced by pressurizing the pressure chamber 23, which is formed by the double bellows 24 which is limited by mutually opposite surfaces of the displaceable nozzle holder 8 and the stationary nozzle assembly 6.
  • the pressure chamber 23 is connected via a bore 34 on the nozzle block side and a pressure line 35 connected thereto to a storage space 36 arranged outside the burner nozzle 3, from which a pressure medium, for example in the form of a hydraulic fluid, can be displaced depending on the load.
  • the storage space 36 is limited in the illustrated embodiment by a single bellows 37, which is arranged in a chamber 38 filled with a refrigerant, which is load-dependent by means of an associated heating device 39, i. H. can be heated in such a way that if the temperature rise rate is too high, heat is transferred to the chamber 38 in the heat exchanger assigned to the burner nozzle 3.
  • the refrigerant contained in the chamber 38 expands, as a result of which the bellows 37 is compressed and hydraulic fluid is thus displaced from the storage space 36 and fed into the pressure chamber 23.
  • the hydraulic fluid fed into the pressure chamber 23 causes the double bellows to expand.
  • a heating device 15 which is formed by a centrally arranged heating element, is also provided for heating the oil passing through the channel 16 and thus for reducing the viscosity of the oil.
  • the heating device 15 assigned to the annular gap 16 and the heating device 39 assigned to the chamber 38 accommodating the storage space 36 can expediently be controlled in parallel.
  • the nozzle assembly 6 with nozzle holder 8 and injection nozzle 7 serves as an actuator, the movement of which influences the effective oil pressure and the air throughput is used for this purpose, the nozzle assembly 6 is slidably mounted and connected via a rod 41 to the movable wall 42 of a pressure chamber 43 arranged outside the burner nozzle 3.
  • the pressure chamber 43 is provided with a refrigerant charge, the temperature of which can be influenced as a function of the load by means of an associated heating device 44.
  • the heating device 44 can be controlled parallel to a heating device 15 provided in the area of the nozzle holder 8 in order to influence the temperature and thus the viscosity of the heating oil passing through the burner nozzle 3.
  • a bellows 45 protrudes into the pressure chamber 43, the end wall of which on the chamber side forms the movable chamber wall 42 and is connected to the rod 41.
  • the bellows 45 is compressed due to expansion of the refrigerant in the pressure chamber 43 and vice versa.
  • the return movement is supported by a return spring 46.
  • a cylinder-piston arrangement could of course also be used.
  • the movements of the wall 42 are transmitted to the actuator via the rod 41.
  • the combustion air can be controlled via an orifice attached to the nozzle block 6, which cooperates with an associated constriction on the air pipe side, or, as here, transmitted to a corresponding metering device via a linkage 47 carried by the nozzle block 6 or an electrical, optical or pneumatic scanning or the like.
  • a regulating valve 48 is provided in the exemplary embodiment shown, which is arranged in the area of an inlet connection 49 attached to the nozzle block 6, which is connected via a movable hose 50 to a pump (not shown here).
  • the regulating valve 48 is provided with a regulating lever 51 which interacts with a stationary leading edge.
  • the regulating lever 51 simply reaches through an associated recess of a tab 52, which is fastened to the housing of the pressure chamber 43, which can be fixed in a stationary manner on the oil burner housing.
  • the regulating lever 51 is pivoted and the oil pressure is accordingly reduced or increased.
  • the oil pressure serves as a reference variable for the actuator for influencing the air throughput.
  • the viscosity of the oil can be influenced by a heating device controlled in parallel.
  • the actuator is formed by the nozzle holder 8, the single bellows 52 surrounding the centrally arranged heating device 15 is provided opposite the stationary nozzle assembly 6 and nozzle holder 8, which includes a pressure chamber 53 into which the oil flow path forms the pressure port 9 acted upon channel 16 opens and is therefore acted upon directly with heating oil.
  • the pressure chamber 53 is connected via an annular gap 54 directly to the space 55 in front of the injection nozzle 7.
  • the cross section of the annular gap 54 is dimensioned here in such a way that there is no or a predetermined throttling effect.
  • the pressure of the heating oil acting on the pressure chamber 53 brings about an enlargement or reduction of the pressure chamber 23, which is manifested by an expansion or contraction of the bellows 52 and thus by corresponding displacements of the displaceably mounted nozzle holder 8 forming the actuator.
  • the oil pressure is set in the area in front of the pressure chamber 53 as a function of the load, so that the nozzle holder 8 forming the actuator performs load-dependent movements which can be tapped for the load-dependent control of various control variables.
  • a regulating valve 57 is provided in the area of the pressure port 9 acted upon by a pump 56, which can be adjusted by means of a servomotor 59 which is controlled as a function of the load via a regulator 58.
  • the control of the servomotor 59 can take place parallel to the control of the heating device 15 provided for reducing the viscosity.
  • the regulating valve 57 could also be arranged in the area of the return port of the pump 56.
  • pumps with a constant delivery volume can be used.
  • solenoid valves are used for pressure control.
  • the pressure port 9 acted upon by the pump 56 is provided with a relief port 60.
  • a valve is arranged in each case 61 and 62 which are engageable by means of associated actuating magnets 63 in the opening or closing position.
  • the actuating magnets 63 can be controlled via a controller 58 such that the pressure in the pressure connection 9 here increases or decreases stepwise analogously to the load, ie the heat requirement of an assigned heat exchanger.
  • the valve 62 assigned to the relief port 60 is in the closed position.
  • this valve 62 is opened, as is the valve 61 associated with the pressure port 9.
  • this valve 62 is opened, as is the valve 61 associated with the pressure port 9.
  • a two-stage control is provided for the sake of simplicity. However, increasing the number of stages would be possible by increasing the number of valves. If a heating device 15 indicated here by a heating coil is provided for influencing the oil viscosity, this can be controlled parallel to the actuating magnet 63, as is indicated by the dashed signal line 64.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)

Claims (32)

1. Brûleur à huile de petite capacité avec une tête d'injecteur (3) adjointe à un échangeur de chaleur (1), tète qui présente au moins un injecteur (7) relié à une alimentation en huile et fixé par un support d'injecteur (8) de position centrale fixable sur un porte-injecteur (6) et une rampe à brûleur (4) externe comprenant le support de l'injecteur (7) formant un canal d'air de combustion (5) relié à une alimentation en air, dans lequel le débit d'huile est réglable par l'injecteur (7) sous forme d'injecteur de torsion sans retour à section constante et le débit d'air gui correspond au débit d'huile momentané est réglable par le canal d'air de combustion (5) en fonction de la charge et dans lequel est prévu un vérin déplaçable contre une force de rappel, servant au moins à régler le débit d'air, à déplacement axial, caractérisé en ce que dans la zone de passage du flux d'air de combustion dans la rampe à brûleur (4) il est prévu au moins un étranglement (12) formé par une striction (14) et un obturateur (13) agissant avec celle-ci que l'on peut actionner par le vérin positionne dans la tête d'injecteur (3), vérin qui est soutenu par un soufflet (24 ou 52) positionné également dans la tête d'injecteur (3) de manière concentrique à l'axe de l'injecteur à une pièce fixe de la tête de l'injecteur (3) et qui est, en outre, déplaçable par une limitation du mouvement du soufflet (24 ou 52), en fonction de la charge et que l'on peut toujours au moins réduire ou grossir proportionnellement à la pression de l'huile présente dans la zone du passage du flux conduisant à l'injecteur (7).
2. Brûleur à huile de petite capacité selon la revendication 1 caractérisé en ce que le débit d'huile est réglable selon la charge par une constante influence de la pression et de la température de l'huile au niveau de l'injecteur (7) et dans lequel le débit d'huile correspondant à la température de l'huile la plus haute et à la pression d'huile la plus basse est choisi de telle sorte à assurer une finesse de pulvérisation suffisante.
3. Brûleur à huile de petite capacité selon la revendication 1 caractérisé en ce que, dans le cas où le flux d'air passant dans la rampe à brûleur (4) est divisé en un courant d'air primaire passant par un réducteur de pression (10) placé du côté de la sortie d'air et en un courant d'air secondaire contournant le réducteur de pression (10), celui- ci est réglable en fonction de la charge.
4. Brûleur à huile de petite capacité selon la revendication 3 caractérisé en ce que le réducteur de pression (10) dont le bord externe forme un étranglement (11) avec une striction de la rampe à brûleur (4) du côté de la sortie de l'air est fixé au vérin (support d'injecteur 8).
5. Brûleur à huile de petite capacité selon la revendication 3 caractérisé en ce que le courant d'air secondaire est décalé par rapport au courant d'air primaire par une conduite d'air (69) concentrique dans la rampe à brûleur (4), conduite qui a la forme d'un tube télescopique qui mène d'une part au réducteur de pression (10) stationnaire et est fixé d'autre part au vérin (bague 30) et porte dans sa circonférence externe un obturateur (13) pénétrant dans le courant d'air secondaire et agissant avec une striction (14) de la rampe à brûleur (4).
6. Brûleur à huile de petite capacité selon l'une des revendications 3 à 5 caractérisé en ce que est monté sur le porte-injecteur (6) un support d'injecteur (8) déplaçable portant l'injecteur (7) et de préférence le réducteur de pression (10), support qui limite le soufflet (24 ou 52) pour former le vérin, qui d'autre part est limité par le porte-injecteur (6).
7. Brûleur à huile selon la revendication 6 caractérisé en ce que le support d'injecteur (8) est relié de manière fixe au porte-injecteur (6) et que dans la zone de liaison (manchon 68) sont prévues des fentes de passage (31) pour des supports (32) agissant sur la limitation du soufflet (bague 30) formant le vérin et supportant l'obturateur (13) et/ou la conduite d'air (69).
8. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que dans la zone de passage du courant (canal 16) de l'huile est prévu un étranglement (18) formé par deux surfaces hermétiques (19 ou 20) que l'on peut presser l'une sur l'autre avec une force variant suivant le déplacement du vérin (support d'injecteur 8, bague 30) et situées de préférence près de l'injecteur.
9. Brûleur à huile de petite capacité selon l'une des revendications 1 à 8 caractérisé en ce que le soufflet (24) est placé dans la zone du côté du vérin (bague 30) faisant face au porte-injecteur (6).
10. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que le soufflet (24) a, de préférence, la forme d'un double soufflet cylindrique.
11. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que le soufflet (24) s'accrochant au vérin (support d'injecteur 8, bague 30) peut être soumis à l'injection d'un produit de pression repoussable d'une chambre de retenue (36) en amont en fonction de la charge.
12. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que le soufflet (24) s'accrochant au vérin (support d'injecteur 8, bague 30) est rempli d'un réfrigérant pouvant se réchauffer suivant la charge.
13. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que le mouvement du vérin (support d'injecteur 8, bague 30) agissant sur le débit d'air et d'huile est réglable à l'aide de la température de l'huile fournie à l'injecteur (7) et variable selon la charge.
14. Brûleur à huile selon la revendication 12 caractérisé en ce qu'un dispositif de chauffage (15) placé de préférence au centre et entouré par le soufflet (24 ou 52) est prévu pour chauffer l'huile et peut être alimenté en énergie en fonction de la charge.
15. Brûleur à huile de petite capacité selon la revendication 14 caractérisé en ce que le dispositif de chauffage (15) destiné à l'huile peut être mis en contact de conduction de chaleur avec le soufflet (24) se remplissant d'un réfrigérant par l'intermédiaire de l'huile de passage.
16. Brûleur à huile de petite capacité selon les revendications 14 ou 15 caractérisé en ce que le thermoplongeur formant le dispositif de chauffage (15) peut se déplacer dans le sens axial et radial et porte un organe de fermeture (bille 75) agissant avec un joint (disque 74) stationnaire.
17. Brûleur à huile de petite capacité selon les revendications 15 ou 16 caractérisé en ce que le passage du flux (canal 16) de l'huile vers l'injecteur (7) par un tuyau de pression (9) s'ouvrant dans la zone du porte-injecteur (6) et relié à une pompe traverse dans la zone entre le dispositif de chauffage (15) situé au centre et le soufflet (24) l'entourant.
18. Brûleur à huile de petite capacité selon l'une des revendications ci-dessus caractérisé en ce que dans la zone de la section placée du côté du porte-injecteur du passage du flux de l'huile conduisant à l'injecteur (7) se trouve au moins un filtre à huile (29 ou 29a).
19. Brûleur à huile de petite capacité selon l'une des revendications 14 à 18 caractérisé en ce qu'une surface (20) du vérin (18) est prévue du côté du porte-injecteur à l'extrémité d'un tuyau (26) placé entre le dispositif de chauffage (15) et la chambre de pression (23), fabriqué dans un matériau thermoconducteur et déplaçable qui peut être soumis à une injection dans le sens de fermeture à l'aide d'une force de fermeture fournie de préférence par un ressort de fermeture (21 ).
20. Brûleur à huile de petite capacité selon la revendication 19 caractérisé en ce que la surface hermétique (20) située du côté du tuyau agrippe une surface hermétique (19) correspondante du support de l'injecteur (8) et que l'extrémité du tuyau faisant face à la surface hermétique (20) agrippe une contre-surface du porte-injecteur (6) stationnaire et y est soutenue par le ressort de fermeture (21).
21. Brûleur à huile de petite capacité selon la revendication 19 ou 20 caractérisé en ce que le tuyau (26) est en contact thermique avec le dispositif de chauffage (15) étanche.
22. Brûleur à huile de petite capacité selon les revendications 19 ou 20 caractérisé en ce que le tuyau (26) est placé sur le dispositif de chauffage (15) avec un jeu radial et est étanche par rapport au support d'injecteur (8) stationnaire et agrippe avec sa surface hermétique une surface hermétique correspondante du dispositif de chauffage (15) situé au centre et que l'extrémité du tuyau (26) faisant face à la surface hermétique agrippe le vérin mobile (bague 30) situé en face du support d'injecteur (8) stationnaire et le soutient à l'aide du ressort de fermeture (21).
23. Brûleur à huile de petite capacité selon la revendication 22 caractérisé en ce que la force correspondant à la pression d'arrêt du soufflet (24) est supérieure à la force du ressort de fermeture (21).
24. Brûleur à huile de petite capacité selon la revendication 23 caractérisé en ce que le vérin (30) est relié à un élément stationnaire (porte-injecteur 6, support d'injecteur 8) opposé au soufflet double (24) à l'aide d'un soufflet simple (33) enveloppant le ressort de fermeture (21).
25. Brûleur à huile de petite capacité selon les revendications 19 à 24 caractérisé en ce que le tuyau (6) présente sur sa surface hermétique un prolongement (27) raccordé qui limite une fente annulaire (28) raccordée à l'étranglement (18) et enveloppe un filtre (29) en amont de l'injecteur (7).
26. Brûleur à huile de petite capacité selon l'une des revendications 1 à 7 caractérisé en ce que le soufflet (52) présente une fente de sortie (54) de section constante et peut être soumis à l'injection d'huile dont la pression dans la zone du soufflet (52) est réglable en fonction de la charge.
27. Brûleur à huile de petite capacité selon la revendication 26 caractérisé en ce que le soufflet (52) a la forme de l'intérieur d'un soufflet simple (52) traversé par de l'huile.
28. Brûleur à huile de petite capacité selon les revendications 26 ou 27 caractérisé en ce que dans un tuyau de pression (9) et/ou des tuyaux de retour (60) en aval d'une pompe, il est prévu au moins une soupape de commande (57 ou 61 ou 62 ou 48) qui est réglable selon la charge.
29. Brûleur à huile de petite capacité selon la revendication 28 caractérisé en ce que la soupape de commande (48) est reliée au vérin, de préférence avec le porte-injecteur (6) déplaçable formant le vérin et présente un élément de commande (51) qui agit avec un élément stationnaire (52).
30. Brûleur à huile de petite capacité selon la revendication 29 caractérisé en ce que la soupape de commande (57) est réglable à l'aide d'un moteur de réglage (59) fonctionnant en relation avec la charge.
31. Brûleur à huile de petite capacité selon la revendication 29 caractérisé en ce qu'un tuyau de décharge (60) part du tuyau de pression (9) et qu'au moins le tuyau de décharge (60) est bloca- ble à l'aide d'au moins une soupape (62) réglable en fonction de la charge.
32. Brûleur à huile de petite capacité selon une des revendications 28 à 31 caractérisé en ce que la pompe (56) a la forme d'une pompe réglable suivant la charge et est de préférence à plusieurs étages.
EP84102707A 1983-03-16 1984-03-13 Brûleur à huile de petite capacité Expired EP0122454B1 (fr)

Priority Applications (1)

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AT84102707T ATE41500T1 (de) 1983-03-16 1984-03-13 Kleinoelbrenner.

Applications Claiming Priority (2)

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DE3309301A DE3309301C2 (de) 1983-03-16 1983-03-16 Ölbrenner
DE3309301 1983-03-16

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EP0122454A1 EP0122454A1 (fr) 1984-10-24
EP0122454B1 true EP0122454B1 (fr) 1989-03-15

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US (1) US4651928A (fr)
EP (1) EP0122454B1 (fr)
AT (1) ATE41500T1 (fr)
DE (2) DE3309301C2 (fr)
WO (1) WO1984003752A1 (fr)

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Also Published As

Publication number Publication date
US4651928A (en) 1987-03-24
DE3477254D1 (en) 1989-04-20
EP0122454A1 (fr) 1984-10-24
DE3309301A1 (de) 1984-09-20
WO1984003752A1 (fr) 1984-09-27
DE3309301C2 (de) 1986-04-10
ATE41500T1 (de) 1989-04-15

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