EP0764254B1 - Bruleur a mazout - Google Patents

Bruleur a mazout Download PDF

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Publication number
EP0764254B1
EP0764254B1 EP95924243A EP95924243A EP0764254B1 EP 0764254 B1 EP0764254 B1 EP 0764254B1 EP 95924243 A EP95924243 A EP 95924243A EP 95924243 A EP95924243 A EP 95924243A EP 0764254 B1 EP0764254 B1 EP 0764254B1
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EP
European Patent Office
Prior art keywords
valve
oil burner
burner according
piston
fuel
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 - Lifetime
Application number
EP95924243A
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German (de)
English (en)
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EP0764254A1 (fr
Inventor
Wolfgang Heimberg
Wolfram Hellmich
Franz Kögl
Reinhold Ficht
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Ficht GmbH and Co KG
Original Assignee
Ficht GmbH and Co KG
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Publication of EP0764254A1 publication Critical patent/EP0764254A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/02—Liquid fuel
    • F23K5/06—Liquid fuel from a central source to a plurality of burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/02—Liquid fuel
    • F23K5/04—Feeding or distributing systems using pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M20/00—Details of combustion chambers, not otherwise provided for, e.g. means for storing heat from flames
    • F23M20/005—Noise absorbing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
    • F23R2900/00014—Reducing thermo-acoustic vibrations by passive means, e.g. by Helmholtz resonators

Definitions

  • the invention relates to an oil burner for thermal systems according to the preamble of claim 1.
  • a burner is known from document DE-A-2 354 708.
  • Oil burners for thermal systems traditionally include a combustion chamber into which a nozzle continuously Fuel is supplied.
  • Oil burners especially large burners, experience resonance vibrations on, the vibration behavior in oil burners caused by the combustion chamber and the type of air supply that together form a sound box.
  • Such pulsed burners can make an enormous noise cause that is between about 90 and 140 dB (A). That's why a system was provided in WO 92/08928 that the resonance system from combustion chamber and fuel supply line acoustically decoupled from the downstream heat exchanger.
  • the one with these pulsed burner resonance frequency is about at some 100 Hz and depends on the shape and size of the through the combustion chamber and the feed lines formed cavities.
  • oil burners are known to have gas burners bad exhaust gas values, on the one hand due to the contained in the oil Components and secondly by poorer atomization of the sometimes viscous oil in the combustion chamber be so that it is difficult to get a full stoichiometric To achieve combustion.
  • the oil supply lines also drip for continuous oil supply after, resulting in poor Combustion leads in terms of exhaust gas values.
  • fuel injectors are usually designed as a pump-nozzle system. As pumps become electromagnetic operated pumps where the reciprocating piston is used the pump is driven by an electromagnet Anchor is applied. There are also various pumps with piezoelectric Actuators known.
  • DE-OS 23 07 435 is a fuel injection device described for internal combustion engines in which the pump work space by an electrically driven reciprocating pump with the Pressure chamber of at least one hydraulically operated spring-loaded Injector connected and via an inlet valve a pressure source is connected.
  • the pump piston closes Start of the pumping process in a certain idle stroke, whereby the Mass of the pump piston accelerates before the actual pump stroke and the stored kinetic energy to increase the pressure is used in the pump work room.
  • the Injector as a pump piston before a soft iron anchor, by a linear motor over a relatively long distance is driven.
  • the piston is penetrated by the delivery piston Fuel conveyor in a first section with axially arranged Provide grooves through which the fuel can drain can, without there being a substantial pressure build-up, the in the subsequent second section of the conveyor, that has no fluid drainage grooves.
  • the delivery piston is therefore slowed down by the incompressible fuel, whereby a pressure is built up in the fuel, through which the Resistance of the injector is overcome, so that it Fuel injection is coming.
  • the disadvantage here is that when the delivery piston is immersed in the closed section of the feed cylinder due to unfavorable gap conditions, namely a large gap width and a small gap length, Large pressure drops occur which create the necessary pressure adversely affect for hosing down.
  • Another fuel injection device is known from WO 93/18297 out, according to the solid-state energy storage principle works, one in a pump cylinder with one Reciprocating piston driven solenoid driven piston element Parts of the fuel to be sprayed off during an almost resistance-free acceleration phase during which the piston element stores kinetic energy before hosing down displaced in the pump area and the displacement suddenly to stop the repression, so that a pressure surge is located in a closed pressure chamber Fuel is generated by the stored kinetic Energy of the piston element directly to that in the pressure chamber located fuel is transmitted.
  • the pressure surge becomes Spraying of fuel through an injector device used, the one that interrupts the displacement, the pressure surge generating agent outside the leading, liquid-tight Contact area between the piston element and the piston cylinder the reciprocating pump are arranged, thereby controllability with high frequency and excellent accuracy of delivered amount of fuel is reached. In particular can even small amounts of fuel can be dispensed precisely.
  • Another fuel injection device for internal combustion engines, that works on the energy storage principle is over WO 92/14925 known. The structure of such a conventional one The injection device is described below with reference to FIG. 23 described in more detail.
  • a fuel tank 601 is turned into a fuel pump 602 with a pressure of approximately 3 to 10 bar Fuel is fed into a pipeline 605, in which a Pressure regulator 603 and a damping device 604 arranged are.
  • a pressure regulator 603 and a damping device 604 arranged are At the end of the line 605 .
  • an electromagnetic, for example operated shut-off valve 606 provided, via which Fuel accelerated by pump 602 when open is returned to the reservoir 601.
  • the size the resulting pressure surge is about 20 to 80 bar, that is about ten times the flow pressure generated by the pump 602 on line 605, also called the swing line becomes.
  • the pressure surge thus created at the shut-off valve 606 becomes The fuel accelerated in this way is sprayed over an injector 610 used, which via a pressure line 609 connected to valve 606 and thus to line 605 is.
  • this known injection device is electronic controllable by means of one connected to the valve 606 electronic control unit 608.
  • the injector With this basic structure of the injector, the it works with an energy stored in the fuel disadvantageous that a pre-pressure supply is required, which the for the acceleration of the fuel liquid column in the necessary energy to the swing line, and which works continuously.
  • This continuously working pre-pressure supply makes a corresponding effort for education constant maintenance is necessary.
  • the Pump 602 too much fuel delivered via the pressure control valve 603, which is connected via a return line to the Reservoir 601 communicates.
  • This pressure cutoff leads to a loss of energy, and thus in addition to an increase the fuel temperature to pressure changes at the injection valve 606, which affects the accuracy of the injection becomes.
  • the pressure control valve 603 always needs a minimum regulation quantity in order to work stably, whereby another loss of energy occurs.
  • the pressure supply unit Because the volume flow requirement on the injector 10 depends on the engine speed, and the quantity to be sprayed, the pressure supply unit the flow rate for full-load operation already at idle promote, whereby relatively large amounts of fuel with appropriate Energy loss for the entire system via the pressure control valve 603 must be shut down.
  • WO 92/14925 proposes that for injection required fuel volume flow for each injection process to be provided only as long as this depends from the engine operating conditions according to time and quantity requirements is required.
  • an intermittent operated fuel acceleration pump is eliminated continuous supply of pre-pressure, which is the energy balance of the Injector benefits.
  • Utilization is optimized the energy further through the use of a common control device for the acceleration pump and the electrically operated Delay device, for example in the form of a Electromagnetically actuated shut-off valve.
  • an intermittently operating fuel acceleration pump an electromagnetically operated piston pump used.
  • it can also be a diaphragm pump for fuel acceleration provided within the pressure surge device will.
  • an electromagnetic pump drive can also be an electrodynamic, a mechanical or a Drive means piezo element may be provided.
  • the invention has for its object an oil burner for to create a thermal system with which it is possible Avoid pressure vibrations safely and excellent exhaust gas values to reach.
  • the task is accomplished by an oil burner with the features of the claim 1 solved.
  • an oil burner with an injector, which works according to the energy storage principle from a pump and a nozzle or a valve that a defined Quantity of fuel is suddenly injected into the combustion chambers, can occur with conventional oil burners Pressure vibrations in the resonance range thanks to precise control the frequency can be prevented. This is mainly due to the Energy storage principle achieved, the delivery is very short High frequency and high pressure pulses allowed. By the high pressure will also atomize the fuel very well achieved in the combustion chamber and a very precise dosage, whereby the pollutant values are kept low.
  • the one forced by the injection process Frequency chosen so that the frequency distance from the resonance frequency the combustion chamber is as large as possible.
  • the injection device By providing the injection device according to the invention it is possible for the first time with a previously unknown Accuracy to control the amount of oil supplied to the combustion chamber or to regulate, whereby an exact setting of the oil / air ratio is possible, so that a stoichiometric combustion ratio or one with excess air can to keep the pollutants in the exhaust gas low.
  • the success of the device according to the invention is based on The fact that the vibrations and pollutants that occur not through compensating devices such as one Vibration decoupling, to be fought, but directly on site the creation by controlling the flame itself be prevented.
  • compensating devices such as one Vibration decoupling
  • the sudden supply of the oil by the injection device according to the invention enables injection pulses from less than 10 ms to in the order of 1 ms, so that they are suitable for the counteract usual resonance vibrations of a few 100 Hz.
  • the quick response of the injection device according to the invention also reliably prevents overshoot the control of the oil supply, that of conventional oil burners could not be avoided and leads to increased exhaust gas values.
  • the oil burner according to the invention can be fast Response behavior operated in a closed control loop with a gas sensor in the fireplace or in the combustion chamber the resulting gases are measured and determined to be as low in pollutants as possible Regulates values with high thermal efficiency.
  • gas sensors can be sensitive to oxygen or carbon monoxide, for example be.
  • the injector preferably comprises one by one Electromagnet driven pump, in particular in oil burners Large burners, necessary pumping capacity of some kg / h up to 900 kg / h.
  • Electromagnet driven pumps based on the solid-state energy storage principle work, include one with an electromagnet driven piston pump with one in a pump cylinder guided piston element, the subsets of the sprayed Fuel during an almost resistance-free Acceleration phase during which the piston element is kinetic Stores energy before hosing down in the pump area displaced and the repression suddenly with the repression interrupting means is stopped, so that a pressure surge in fuel located in a closed pressure chamber in which the stored kinetic energy of the piston element directly on the fuel in the pressure chamber is transmitted.
  • the pressure surge becomes a spray of fuel used by an injector device.
  • Those based on the solid-state energy storage principle are particularly advantageous fuel injectors working when the pressure generating means outside the leading one liquid-tight contact area between the piston element and reciprocating cylinder of the reciprocating pump are arranged so that in a simple way a practically wear-free one Injector is obtained with very short injection pulses larger amounts of fuel in the combustion chamber can inject.
  • the oil burners according to the invention are based on the energy storage principle working injector provided a defined amount of oil is suddenly injected into the combustion chamber.
  • the injection devices working according to the energy storage principle can be divided into two subgroups, the Injectors that are in the accelerated fuel use stored energy, and those based on the solid-state energy storage principle work.
  • the injection pump is provided, in which the displacement of the Fuel does not result in pressure build-up, whereby the Conveyor element stroke serving for energy storage advantageously through a storage volume e.g.
  • a stop element in the form of an empty volume and a stop element is determined, which is based on the following of the exemplary embodiments is different can be designed, for example in the form of a spring-loaded Membrane or a spring-loaded piston element, against which fuel is pumped and which is on a stroke "X" allow the delivery element to displace fuel; first then when the spring-loaded element is on during the displacement one e.g. abuts a firm stop, there is an abrupt pressure build-up generated in the fuel, so that a displacement of the fuel in the direction of the injector.
  • the delivery line 2 branches off an intake line 4, which with a fuel reservoir 5 (tank) is connected.
  • the delivery line 2 is approximately in the area of the connection the suction line 4 a volume storage element 6 via a line 7 connected.
  • the pump 1 is designed as a piston pump and has a housing 8, in which a magnet coil 9 is mounted, one in the area of the coil passage arranged anchor 10, which as a cylindrical body, for example, designed as a full body and in one Housing bore 11 is guided, which is in the region of the central longitudinal axis the ring coil 9 is located, and by means of a compression spring 12 is pressed into a starting position in which it is on Bottom 11a of the housing bore 11 abuts.
  • The is supported Compression spring 12 on the end face of the injection nozzle Armature 10 and a ring step opposite this end face 13 of the housing bore 11.
  • the spring 12 includes with play a delivery piston 14 which is connected to the armature 10 by the spring 12 loaded anchor face, e.g.
  • the delivery piston 14 plunges relatively deep into one cylindrical fuel delivery chamber 15, which is coaxial in axial Extension of the housing bore 11 is formed in the pump housing 8 and is in transmission connection with the pressure line 2 stands. Due to the immersion depth, pressure drops can occur during of the sudden pressure rise can be avoided, the Manufacturing tolerances between the piston 14 and cylinder 15 even can be relatively large, e.g. only in the hundredth of a millimeter range need to lie, so that the manufacturing cost is low.
  • a check valve 16 is arranged in the intake line 4.
  • the housing 17 of the valve 16 is, for example, as a valve element a ball 18 arranged by in its rest position a spring 19 against its valve seat 20 on the reservoir side End of the valve housing 17 is pressed.
  • the spring 19 is supported on the one hand on the ball 18 and on the other hand on the wall of the valve seat 20 opposite Housing 17 in the area of the mouth 21 of the intake line 4th
  • the storage element 6 has e.g. two-part design Housing 22, in its cavity as an organ to be displaced a membrane 23 is stretched, which from the cavity a pressure line side, separates the space filled with fuel, and which divides the cavity into two halves when relaxed, which are sealed against each other by the membrane.
  • a spring force acting on it e.g. a spring 24, which acts as a return spring for the membrane 23 is set up.
  • the spring 24 is opposite to the membrane End on an inner wall of the cylindrical widened empty cavity stored.
  • the empty cavity of the housing 22 is delimited by an arched wall, the one Forms stop surface 22a for the membrane 23.
  • the coil 9 of the pump 1 is connected to a control device 26, that as electronic control for the injector serves.
  • the armature 10 is in the de-energized state of the coil 9 Pump 1 by the bias of the spring 12 on the bottom 11a.
  • the Fuel feed valve 16 is closed and the storage membrane 23 is by the spring 24 in its from the stop surface 22a held in the withdrawn position in the housing cavity.
  • the coil 9 is switched off. Of the Armature 10 is moved back to the bottom 11a by the spring 12. The amount of liquid stored in the storage device 6 via lines 7 and 2 in the feed cylinder 15 sucked back and the membrane 23 due to the action of Spring 24 pushed back into its original position. At the same time opens the fuel feed valve 16 so that fuel from the Tank 5 is sucked up.
  • valve 16a is arranged, a stand pressure in the injector side space which e.g. is higher than the vapor pressure of the liquid at maximum temperature, so that bubbles form is prevented.
  • the parking pressure valve can e.g. as the Valve 16 may be formed.
  • a displacement element for the memory element 6 can instead of Membrane 23 also a storage piston 31 can be used.
  • the attack, which suddenly stops saving in this case be adjustable according to the invention so that the path length the acceleration stroke of armature 10 and delivery piston 14 can be changed.
  • This adjustment is for example carried out manually by an adjusting element, which has a Cable 40 transmits the adjustment path to a displacement piston 31.
  • the adjustment can be carried out expediently the control device 26, for example by means of an actuating magnet being controlled.
  • Figure 2 shows e.g. an embodiment of the storage element 6 with a cable 40 adjustable displacement piston 31.
  • the drain hole 32 is in the cylinder wall of the Housing 30 formed in the region of the housing cover 33, the opposite the housing wall 33a, which is integrally formed with a wall section of the pressure line 2.
  • the drain hole 32 extends approximately radially to the central longitudinal axis 33b of the cylindrical Housing 30.
  • the housing cover 33 of the housing 30 is in the axial direction elongated tubular, and in the passage of the extension tube 36 a piston pin 37 is slidably guided like a piston has a ring 38 at the end located in space 33c. against the bottom of the ring 38 pushes the piston 31 when it is out its rest position in the direction of the housing cover 33 moves becomes.
  • This stop element 37 is biased by a spring 39 stored.
  • the spring 39 is supported for this purpose on the one hand on the inside of the cover 33 and on the other hand the ring step of the ring 38 of the bolt 37.
  • the cable pull 40 On the outside of the Part of the bolt 37 arranged in the cylinder 30 is the cable pull 40 attached.
  • the stop pin 37 is in via the cable 40 Adjustable in the direction of the central longitudinal axis 33b of the housing 30, so that the possible stroke of the piston 31 of the position of Stop ring 38 can be varied accordingly.
  • the stop pin 37 can, depending on the required acceleration stroke the armature 10 of the pump 1 (Fig. 1) can be adjusted.
  • the mode of operation of the memory element 6 according to FIG. 2 corresponds essentially that of the memory element 6 Fig. 1.
  • the return spring 34 relative is soft, so that the 10th by the anchor seated delivery piston 14 moving fuel with almost no resistance of the storage piston 31 can be displaced. This will the armature 10 with delivery piston 14 almost on part of the stroke resistance-free, i.e.
  • the adjustable stop pin 37 is also suitable for exclusive Control of the amount of fuel to be injected.
  • the fuel feed valve (valve 16 in FIG. 1) to be designed so that it also acts as a storage element (corresponding to storage element 6 in Fig. 1 and 2), so that fuel almost resistance-free on the first partial stroke of the delivery piston from the delivery cylinder 15 and the pressure line 2 into a storage volume is derived, this storage element also determines the distance of the first partial stroke of the delivery piston 14.
  • Fig. 3 shows a first embodiment of such Trained fuel feed valve, which is also the function a storage element for determining the first partial stroke of the Delivery piston guaranteed.
  • the valve 50 comprises a substantially cylindrical one Housing 51, in one piece in the illustrated embodiment is formed with the pressure line 2.
  • a through bore 52 is made, the one Pressure line side section 53, which via an opening 53a in the pressure line 2 opens, and a suction-side section 53b, which is connected to the feed line to the fuel tank 5 (FIG. 1) is connected.
  • a radially expanded valve space 54 formed, which receives a shut-off valve element 55.
  • the valve element 55 consists of a circular disk 56 large diameter and a circular disc 57 small diameter, wherein both circular disks are integrally formed and with the circular disk 57 of smaller diameter on the side of the bore section 53 is arranged.
  • a valve body return spring 58 presses the valve element 55 against in the idle state the end face 59 of the valve chamber 54 on the pressure line side, the spring 58 on the one hand on the disk 56 of the valve element 55 and on the other hand supports at the bottom of a ring step 60, that centrally in the face 59 of the valve chamber 54 opposite end face 61 is arranged.
  • the disk 56 can thus seal against the end face 61 of the valve chamber 54 arrive.
  • the bore section 53 of the central longitudinal bore 52 is in Connection to the valve chamber 54 in the housing wall 51 arranged grooves or grooves 62, which in the direction of the valve space 54 can be designed to expand in a funnel shape (see FIG. 3).
  • the valve element lies in the starting position shown in FIG. 3 55 by the action of the spring 58 with the disk 57 on the end face 59 of the valve chamber 54.
  • the reservoir section 53b is above the valve space 54 and the grooves 62 and the bore section 53 in Flow connection with the pressure line 2 and the delivery cylinder 15, wherein the symbolically shown fuel tank device 5 an empty space volume or storage volume in which Fuel can be displaced, provides.
  • the flow conditions of the valve 50 are designed so that at Reaching a certain flow rate of the fuel the flow forces around the fuel Valve element 55 become larger than the biasing force of the spring 58 so that it is pressed to bore 53b. Closes the valve element 55 with the disk 56 the inlet cross section the bore 53b or the recess of the ring step 60, which is a abrupt transfer of the kinetic energy of the armature 10 with piston 14 on the fuel in the feed cylinder 15 and in the Pressure line 2 has the result that fuel through the nozzle 3rd (see Fig. 1) is hosed.
  • this version of the valve device 50 is the energy storage path of the armature 10 with the piston 14 controllable by the excitation of the coil.
  • the valve element 55 lifts by the pressure of the spring 58 from the mouth of the feed line 53b again when the piston 14 or the armature 10 moves back, so that fuel can be sucked out of the tank 5.
  • FIG. 4 shows a variant of the above with reference to FIG. 3 Component described, the function of both the fuel supply as well as the control of fuel injection takes over, in addition the one serving for energy storage Partial stroke of the delivery piston can also be controlled via the component is.
  • an electrically controllable valve 70 used for this purpose.
  • valve 70 has a spring-loaded in a valve housing 77 Valve plate 72, which is firmly connected to an armature 73 is.
  • the armature 73 has a central axis bore 74 and at least a transverse bore 75 in the area of Valve plate 72.
  • valve 70 In the rest position, valve 70 is open, by the armature 73 being pressed against the plate 72 Spring 76 is pressed into a pressure line end position, in of the fuel of the storage container, not shown the holes 75 and 74 and the pressure line opening 71 with the Fuel of the pressure chambers 15, 2 is connected.
  • a coil 78 is also arranged, which Anchor 73 surrounds at a distance.
  • the injection process takes place as follows.
  • the solenoid 9 of the Pump 1 excited, causing the armature delivery piston element 10, 14 of the Pump 1 is accelerated out of its rest position.
  • the from Piston 14 displaced fuel flows through the pressure line opening 71, the central bore 74, the transverse bore 75 around the Valve plate 72 around and in the tank-side part of the line 4 to the fuel tank.
  • valve 70 is activated by energizing coil 78 and armature 73 is moved until the valve plate 72 assumes its valve seat and blocked the fuel path.
  • the pressure line opening 71 is blocked suddenly or very quickly, so that none further fuel can escape via line 4.
  • Anchor 10 with delivery piston 14 are braked suddenly as a result and give the stored kinetic energy to the incompressible Fuel, which results in a pressure surge the fuel from the pressure line 2 via the injection valve 3 is hosed, as in the other embodiments the invention of the armature 10 with piston 14 either its full Has reached the delivery stroke or is still being moved.
  • the injector 3 is hydraulically controlled in a manner known per se and spring-loaded.
  • the control of the valve 70 is preferably carried out via control electronics that work together the pump 1 and the shut-off valve 70 are operated.
  • Fig. 5 shows a modification of the valve of Fig. 3.
  • the integral Storage element inlet valve 90 has a housing 91, that is constructed in a unitary manner with the housing 8 of the pump 1 and the pressure line 2.
  • the housing 91 is a central longitudinal bore 92 introduced, the one end via an opening 93a in the pressure line 2 and otherwise in a cylindrical Valve chamber 93 opens, with channels 94 similar to the channels 62 from FIG. 3 lead from bore 92 to valve chamber 93.
  • the Valve element is formed in two parts and includes an in Valve chamber 93 guided cylinder 95, in the cylindrical, through a central stage bore a piston 96 slidably to be led. In the outer surface of the cylinder 95 are axially parallel grooves 97 are formed.
  • the cylinder 95 is pressed into its rest position by a spring 98, in which he with his one end face on the tank side Bottom of the valve chamber 93 sits in the one of the fuel tank Coming fuel supply line 99 opens.
  • the piston 96 against the pressure line side bottom of the Valve chamber 93 presses so that the bore 92 is covered, with a free space in the interior of the cylinder 95 on the tank side 95a for the piston 96 is formed.
  • the valve 90 works as follows. If the delivery piston 14 executes a suction stroke, fuel from line 99 becomes thereby sucked in that the cylinder 95 from the tank side bottom surface of the valve chamber 93 by the negative pressure against the pressure the spring 98 is lifted off, so that fuel via the longitudinal grooves 97, the valve chamber 93 and the channels 94 and the bore 92 can flow into the pressure line 2. In this process lies the piston 96, as shown in Fig. 5, on the pressure line side Bottom of the valve space 93. At the end of the suction stroke cylinder 95 is moved by spring 98 into that shown in FIG Position pressed in which the cylinder 95 again on the tank side Bottom of the valve chamber 93 lies sealingly.
  • the delivery cylinder becomes 95 guided pistons 96 due to the relatively soft design the spring force of the spring 100 from its abutment on the pressure line side Bottom of the valve space 93 moved away and in the Free space 95a is pressed, the resulting additional ones Space in the valve space 93 Fuel from the pressure space 15, 2 flows, which displaces during the conveying movement of the delivery piston 14 being, on the tank-side end of the piston 96 from piston 96 fuel via line 99 into the tank is pushed back.
  • the delivery stroke of the delivery piston 14 is in that the piston 96 with its tank-side of of the spring 100 loaded end face at the step in the Center longitudinal bore of the piston 95 strikes.
  • the armature 10 with delivery piston 14 is the Formation of a very steep pressure rise in the pressure line 2 causes fuel at high pressure through the nozzle 3rd is hosed.
  • a corresponding embodiment is shown in Fig. 6.
  • A serves as a storage element Accumulator piston 80 in a pressure line-side first Central longitudinal axis step bore section 14b one through centrally the piston 14 and the armature 10 against stepped bore 14a a stop on the pressure line side (not shown) of a spring 81 is pressed.
  • the piston 80 projects in the Rest position with its one end face in the pressure chamber 15.
  • the bore portion 14b receiving the accumulator piston 80 in Delivery piston 14 sits after armature 14c toward armature 10 in a further stepped bore section 14d, on the Stage 14e the compression spring 81 is supported against the armature side End face of the piston 80 presses.
  • the bore 14a finally penetrates anchor 10 and after stage 14e opens into the empty armature space 11, so that air is displaced can.
  • the memory element of this embodiment works like follows. On a first part of the stroke of the delivery piston 14, the Energy storage path, the storage piston 80 in the for Piston provided bore of the delivery piston 14 is pushed in, whereby an additional space for the displaced on the pressure chamber side Fuel is available so that the armature 10 during first stroke section together with the delivery piston 14 substantially can be accelerated without resistance.
  • the no-resistance Acceleration of armature 10 and delivery piston 14 is ended when the anchor-side end face of the accumulator piston 80 against the annular shoulder 14c of the stepped bore 14a is coming. The consequence of this is a sudden increase in pressure, through which fuel is sprayed through the nozzle 3.
  • the injection device according to the invention has a structural Unit of electrically driven reciprocating pump and lifting gear on.
  • FIGS. 7 and 8 is a Hydraulic valve as well as the pump and the pressure line 2 in one common housing 121 housed.
  • the function as well as the essential structure of the pump with electromagnetic drive corresponds essentially to the previously described embodiments the pump 1 of the device according to the invention, wherein the fuel intake takes place via a valve 122 which is fitted in the pump housing 121 and with the pressure line 2 is connected (Fig. 7).
  • the valve 122 closes in the exemplary embodiment shown automatically due to the Bernoulli effect on a specific one Flow rate.
  • the one during the acceleration phase fuel flowing through the pressure line 2 passes through a Gap 123 in the valve chamber 124.
  • fuel flows through this annular gap and creates there after Bernoulli a lower static pressure than in the environment.
  • At a certain flow velocity is the static pressure in the Annular gap has dropped so far that valve cone 125 is tightened is and the valve 122 closes, causing the Fuel pressure surge required via the injector is produced.
  • the pressure line 2 leading to the injection nozzle is connected to the output of a check valve 127, the is also structurally combined with the housing 121.
  • the valve cone 128 of the valve 127 is a by bias Spring 129 pressed against the associated valve seat, the Spring 129 is designed so that valve 127 is closed, if the pressure in the pressure line 2 is below that Value that leads to an emission of fuel over the Injector leads, which is indirectly connected to the valve 127 is.
  • the check valve 127 also causes blistering avoided in the pressure line 2 to the injector valve, because the non-return valve creates a stand pressure in the pressure line guaranteed between the injector and the check valve can be higher than the vapor pressure of the fuel liquid is.
  • the armature 10 is axially parallel in this embodiment Slots 130 and 131 of different depths in the jacket provided that on the circumference of the substantially cylindrical Anchor are arranged distributed. These slots prevent that Formation of eddy currents when exciting the solenoid 9 and thus contribute to energy savings. With a line 120, which leads from the armature space 11 through the housing 121 to the outside, leak oil that has penetrated into the armature space can be extracted.
  • the injection pump armature is reset in the Rule using the provided return spring.
  • To great Achieving spray frequencies is the reset time of the armature to keep small. This can be done, for example, by a corresponding Realize the spring force of the return spring. With however, a reduction in the reset time increases the speed of impact of the anchor at the anchor stop. Disadvantageous the associated wear and / or that Bouncing the anchor on the anchor stop, reducing the total working time is enlarged.
  • An object of the invention is therefore in the fall time of the anchor to the rest position to keep small. According to the invention, this goal is achieved by e.g. hydraulic damping of the armature return movement in the reached the last part of this movement.
  • Fig. 9 shows an embodiment of the injection pump, which in essentially has the structure of the injection pump 1 according to FIG. 1.
  • the armature return movement in a blind cylinder bore 11b in the floor 11a suitably occurs, which on the stop surface lla is formed for the armature 10 in the housing 8.
  • Anchor 10 are longitudinal grooves 10b formed, the anchor back space 11 with the anchor front space 11 connect.
  • the depth of the blind cylinder bore 11b corresponds approximately the length of the projection 10a (dimension Y in FIG. 12).
  • the fact that the projection 10a in the blind cylinder bore 11b can plunge, the armature return movement in the last section greatly delayed, creating the desired hydraulic Damping the armature return movement by displacing the medium from room llb.
  • FIG. 10a shows a variant of the hydraulic damping. Also in this embodiment, that of the delivery piston 14 penetrated pump chamber 11 in front of the anchor 10 connected to the the anchor back adjacent space 11, through holes 10d that in the area of the back of the anchor in a central Overflow channel 10c open.
  • a central pin 8a of a shock absorber 8b protrudes with its cone tip 8c towards the mouth of the overflow channel 10c, a hole 8d passes through in the rear Floor 11a, which opens into a damping space 8e, and ends in Insulation room with a ring 8f, which has a larger diameter has than the hole 8d.
  • One on the floor of the damping room supporting spring 8g presses against the ring 8f and thus the Pin 8a in its rest position (Fig. 10a).
  • a channel 8h connects the insulation space 8e with the rear anchor space 11. Die Channels 10c and 10d allow the armature 10 to be almost resistance-free Movement during the acceleration phase.
  • the damping device 8b is in the acceleration movement of the anchor 10 ineffective, so that no impairment of the Lifting phase.
  • the mouth hits during the return movement the overflow channel to the cone tip 8c and is closed, so that the flow through the channels 10c and 10d is interrupted becomes.
  • the armature 10 presses the pin 8a against the spring force and against the medium in room 8e, which is also in the Room 11 is located and flows out via channel 8h into room 11.
  • the currents and spring forces are chosen so that a optimal damping is guaranteed.
  • a displacement hole can be used according to FIG. 10b 8i be arranged centrally in the pin 8a, through the damping medium can be pressed into the overflow channel 10c.
  • Injector is provided in the return spring 12 of the armature 10 stored energy during the return movement of the anchor 10 to be used to advantage.
  • 11 shows a corresponding exemplary embodiment one connected to the fuel injection pump 1 second pump 260.
  • the fuel injector shown in Fig. 11 is in the 4 are designed according to FIG. and drain control element for controlling the first partial stroke of the delivery piston 14.
  • the second pump 260 is connected to the rear bottom 11a of the pump housing 8 connected. in the individually, the second pump 260 includes a housing 261 which is connected to the housing 8 of the injection pump is connected, and in the Pump chamber 261b a pump piston 262 is arranged, the Piston rod 262a projects into the working space 11 of the armature 10, the piston 262 is acted upon by a return spring 263, which is located on the housing base 261a in the region of an outlet 264 supports.
  • the pump chamber 261b of the housing stands over a supply line 265 in connection with a storage container 266.
  • a check valve 267 is inserted into the feed line 265, the structure of which is similar to that of valve 16 in FIG. 1.
  • the second pump 260 works as follows. If the anchor 10 the injection pump 1 during its working stroke towards the injection nozzle 3 moves, the pump chamber 11 in the housing 8 behind the armature 10 increased in volume, whereby the pump piston 262 is moved in the direction of the armature 10 and finally by the action of the return spring 263 in it Rest position is transferred.
  • the storage container becomes 266 Via valve 267 oil into the working space 261b of the second pump 260 sucked in.
  • the armature 10 of the Pump 1 in the direction of its stop 11a becomes the pump piston 262 at least on part of the return path of the armature 10 pushed into the pump chamber 261b. This is due to the pump pressure the valve 267 is closed and it will be that of the second pump pumped medium via the outlet 264 in the direction of arrow 264a from the pump.
  • the second pump 260 can be used as a fuel back pressure pump are, wherein the fuel of the valve device 70 is supplied can be. It is advantageous that the pump 260 a Stand pressure in the fuel supply system can generate that vapor bubble formation e.g. when the entire system heats up counteracts.
  • FIGs 12a and 12b show a particularly effective and simple Damping device.
  • the structure of the pump device 1 is the same that shown in Figure 9.
  • the blind cylinder bore 11b after Figure 12a is larger in diameter than the diameter of the cylindrical projection 10a.
  • the projection 10a is from a sealing lip ring projecting in the direction of the blind cylinder bore 11b 10e surrounded by an elastic material which in the blind cylinder bore 11b fits.
  • An insertion slope on the Mouth of the blind cylinder bore 11b facilitates the entry of the Lips the sealing lip ring 10e into the blind cylinder bore 11b.
  • This damping device provides good damping when Stop of the armature 10 and hampers the acceleration stroke of the Anchor not.
  • the elastic damping element 10e with axially parallel protruding sealing lips appear during the return stroke of the armature 10 in the blind cylinder bore 11b and lies against the outside of the inner wall of the blind cylinder bore 11b.
  • the blind cylinder bore 11b according to FIG. 12b has a diameter also larger than the cylindrical projection 10a.
  • a sealing ring 10f made of elastic material sits on the Wall of the blind cylinder bore 11b and points in the area of Mouth inward-facing sealing lips 10g.
  • the elastic Sealing element 10f dips the cylindrical projection 10a a piston-like, the sealing lips 10g due to the outflowing Damping medium against the cylindrical projection 10a be pressed so that a particularly good damping of the armature 10 is reached.
  • FIG. 13 shows a likewise compact design of the invention electrically operated piston pump with integrated stop valve. It is in a cylindrical multi-part housing 200 in one of an outer jacket 200a and a cylindrical inner jacket 200b and a tank side End wall 200c and a pressure line end wall 200d delimited interior 202, a coil 201 is arranged.
  • the from Inner jacket 200b surrounding cylindrical interior 202 of the housing 200 is extended by a radially inward Ring 203 in a tank side and a pressure line side Interior area divided.
  • Pressure line side is against Ring edge of the ring 203 a positive and firm in this Set inside ring bead 204 of a piston 205, the piston 205 spacing the ring opening 206 of the ring 203 reaches through and into the tank-side area of the interior 202 protrudes.
  • the piston 205 is from a through bore 207 penetrates, which extends in the tank-side end region of the piston is formed and there stores a valve 208, which by a Coil spring 209 towards the tank side for the closed position is pressed against a valve seat 209a, through with the Exposure to pressure from the tank side opened can be.
  • a pump cylinder 210 of the reciprocating pump On the inside of the tank 202 of the interior 202 located part of the piston 205 sits positively and slidably a pump cylinder 210 of the reciprocating pump, which by a one end on the ring 203 and the other end on a ring step 212 of the cylinder 210 supporting coil spring 211 with its Tank-side end face 214 against a ring step 213 in Inner space 202 is pressed, with a protruding from the end face 214 Valve nozzle 215 with a radial distance a bit in the in this area radially narrowed interior 202a protrudes and where the end face of the cylinder 210 in the pressure line side Distance from the ring 203 is arranged and thus a movement space is created for the cylinder 210.
  • the form-fitting on the Inner walls of the interior 202 are guided cylinders 210 has axially parallel, frontal open longitudinal grooves 216 in the Lateral surface, the function of which is explained below.
  • the continuous through the pump cylinder 210, the piston 205 receiving bore 217 is stored on the tank side of the piston 205 upstream tappet valve, the tappet disc 218 at a distance from the face surface of the piston 205 in a short Hole extension is arranged and its pushrod 219th the narrowed bore 217a in the valve stub 215, against the Supporting inner wall of the bore 217a, reaches through and into the narrowed interior 202a protrudes.
  • the plunger stem 219 still on Extends beyond the plate 220 and against the tank side Bottom surface 222 of the interior 202a abuts.
  • the pestle handle 219 chosen so long that the plunger plate 218 from its Valve seat, the pressure line side opening 223 of the narrowed Bore 217a is lifted off, so that a certain gap "X" is formed whose meaning and purpose is explained below.
  • a coil spring 224 stabilizes this position of the tappet valve in the shown idle position of the reciprocating pump, in which the spring 224 ends on the end face 214 of the Cylinder 210 and otherwise supported against the plate 220.
  • the valve chamber 226 is located with one leading to the fuel tank Fuel line in connection (not shown); to the end wall 200d on the pressure line side or to an extended one A pressure line is attached to the inner wall 200b (not shown), which leads to the spray valve.
  • Fuel line in connection (not shown); to the end wall 200d on the pressure line side or to an extended one
  • a pressure line is attached to the inner wall 200b (not shown), which leads to the spray valve.
  • the arrows drawn in FIG. 13 indicate the path of the fuel on.
  • the reciprocating pump shown in Figure 13 works like follows.
  • the cylinder 210 By energizing the coil 201, the cylinder 210 almost from the shown rest position towards the pressure line accelerated without resistance, from room 202 over the Grooves 216 and from the bore 217 or the tappet plate space Fuel flows out toward interior 202a.
  • the accelerated Movement ends with the impact of the valve seat 223 the valve plate 218 abruptly, so that the stored energy of the Cylinder 210 on the fuel in the plunger vestibule is transmitted.
  • the valve 208 is opened and the Pressure on the one in the bore 207 or in the pressure line Fuel propagated, causing a splash of Fuel is injected through the injector. If the excitement is not yet switched off, fuel is sprayed off for as long as how the cylinder is moved.
  • the tappet valve 218, 219 is taken along by the cylinder 210 and a Vacuum in the interior 202, 202a and in the holes 225 and the anteroom of the valve chamber delimited by valve 229 226 so that the valve 229 is opened.
  • the fuel flows coming from the tank through the peripheral grooves 230 in the valve plate 229, the anteroom of the valve chamber 226, the bores 225 and the Holes 221 in the plate 220 in the interior 202a and over the Grooves 216 in the interior 202.
  • the spring 211 After switching off the excitation the spring 211 returns the cylinder to its rest or home position pushed back, previously the pushrod 219 hits against the bottom wall 222 and opens the tappet valve is so that fuel through the space between the Tappet stem and bore 217a in the plunger plate vestibule 217 can flow.
  • the valve 208 remains closed. It works as a parking pressure valve and stops in between the injection valve (not shown) and the valve plate 208, a space pressure with fuel in the fuel upright, e.g. is higher than the vapor pressure of the liquid at maximum temperature, so that bubbles do not form can be.
  • Piston 205 formed integrally with the end wall 200d and the standing pressure valve 208, 209, which in a pipe socket 208a is housed, covers the mouth of the discharge line bore 207 going through the piston 205.
  • the sliding pump cylinder 210 acting as an anchor is for one simple possibility of mounting the valve lifter 218, 219 constructed in several parts. Since the multiple parts are not essential to the invention is the structure of the cylinder 210 is not closer described.
  • the plunger stem 219 is relatively short and can be over the tank-side end ring surface 214 of the cylinder 210 only by that Protrude valve clearance.
  • the end ring surface 214 abuts in the area the end wall 200c against a plastic block stored there 231, which has through holes 232, the peripheral open into grooves 233, which with the tank-side interior 202 are connected, with 202 holes from the tank-side interior 234 to the enlarged bore area of bore 217 in Guide cylinder 210.
  • the holes 232 open into the tank leading axial valve chamber 226, which in a pipe socket 226a is housed.
  • the tappet valve 218, 219 not spring loaded. It works due to inertial forces, the plunger stem approximately form-fitting in the narrowed bore 217a sits.
  • the tappet valve is positioned by the on the tappet plate 218 acting pressure prevailing in rooms 202, 217, 207 pressed against the plastic block 231. If the cylinder 210 accelerates, the tappet valve remains in this position until it is taken away from the valve seat 223. With the return movement of the armature cylinder 210, the plunger stem 219 abuts against the Plastic block 231 so that the tappet valve is back in its shown starting position arrives.
  • the hole extension expediently forms the hole 217, in which the tappet plate 218 is received, on the pressure line side a ring stage 235, which is in the rest position of the Tappet valve only a short distance in front of tappet plate 218 is located and against which the plunger plate 218 hits when the Tappet due to inertia during the return movement of the cylinder 210 lifts off the valve seat and / or the valve from the plastic block 231 rebounded during the return movement of the cylinder 210 should be.
  • Recesses 235a In the end face of the ring step 235 are Recesses 235a introduced, which has an unimpeded flow ensure the fuel. In this way is the rest position of the tappet valve ensured with simple means.
  • the acceleration of the armature cylinder 210 flows in this embodiment of the injection pump fuel from the pressure line-side interior 202 via the grooves 216 in the Tank-side interior 202 and from the bores 207, 217 through the recesses 235a past the plunger plate 218 through the Valve seat opening in the bores 235 also in the tank side Interior 202.
  • the fuel is displaced by the closing of the tappet valve 218, 219 suddenly interrupted, whereby the intended pressure surge is achieved.
  • With the return movement of the armature cylinder 210 opens the tappet valve 218, 219 and the fuel flows in the opposite direction.
  • the embodiment of the reciprocating piston pump according to FIGS. 14 and 15 can with a simply constructed effective anchor damping device provided, which is shown in Fig. 16.
  • the plunger stem 219 has one in its free end region Flange ring 219a on which the end face 214 a piece overlaps laterally and lie against the end face 214 can.
  • Flange ring 219a In the surface of the plastic block 231 is one Flange ring 219a introduced corresponding recess 231a, in which the flange ring 219a fits approximately form-fitting, so that a piston-cylinder-shaped hydraulic damping device becomes.
  • the thickness of the flange ring 219a is expediently somewhat executed greater than the depth of the recess 231a, so that the Front ring surface 214 in the rest position of the armature cylinder 210 remains at a distance from the surface of the plastic block 231 and support bars are not required.
  • the pressure line side Interior 202 leads to the outside and a nozzle on the outside 237 is set with a through hole 238.
  • a bore 236, the pressure line side Interior 202 leads to the outside and a nozzle on the outside 237 is set with a through hole 238.
  • Through the Bore 236 and drain connector 237 can e.g. during the Start phase of the pump or burner fuel from the anchor cylinder 210 are pumped out, so that the pump and / or Fuel supply line can be flushed out of air bubbles.
  • the sequence 236, 237 can also be used during the injection activity the pump fuel is washed around and thereby Heat is dissipated and bubbles are avoided.
  • cylinder 210 acts as a piston-like anchor element, that is liquid-tight in the inner cylinder 200b becomes.
  • Injection pump 1 One similar to the injection pump shown in FIG. 13 Injection pump 1 is shown in Fig. 17, the same Parts have the same reference numbers.
  • the piston partially seated in the armature cylinder bore 217 205a is not fastened to the end wall 200d on the pressure line side, but axially movable and part of the spray valve device 3.
  • the injection valve 3 has a valve cap 3b, which in the front wall 200d of the housing 200 in the injection valve side Interior 202 is screwed gripping.
  • the valve cap has an injection nozzle hole in the center 3d.
  • the piston 205a covers in its rest position with a Diameter reduced face 205b the injector bore 3a from.
  • the reduced surface area 205b goes with it a truncated cone 205c in the cylindrical part of the piston 205a about.
  • the piston 205a is in the armature cylinder bore 217 from a compression spring 240 against the injector bore 3d pressed, the compression spring 240 against another in the intermediate cylinder 241 arranged in the armature cylinder bore 217 is supported, which bore 217 in an injector side and into a tank-side area.
  • the anchor cylinder in the tank-side area of the interior 202 Grooves on, the groove webs on the inner wall of the interior 202 and there are guides for the armature cylinder 210 form.
  • the pressure surge is applied to the cone surface of the truncated cone 205c transfers and lifts the piston 205 against the pressure of the spring 240 from the nozzle 3a so that fuel is hosed.
  • room 202a and a negative pressure in the tank-side interior 202 which also affects the Piston 205 acts, but is much less than the spring force the spring is 240, so that the piston is unaffected remains.
  • the negative pressure opens the valve 229, so that Fuel is sucked up.
  • the valve 229 closes due to the spring force of spring 228 again when the return movement the armature cylinder 210 begins, so that then by the armature cylinder movement Fuel into the spaces of bore 217 and Interior 202 is pushed.
  • the function of the valve 292 corresponds the function of the same valve 229 in the Embodiment of the injection pump 1 according to FIG. 13.
  • FIG. 18 Another embodiment of the injection pump according to the invention 1, in which the injection nozzle 3 directly in the end wall 200d is housed in the housing 200 of the injection pump 1, results from Fig. 18. This embodiment is similar to that of Fig. 17, which is why the same parts with the same reference numerals Marked are.
  • valve cap 3b forms a valve seat 3c for a tappet valve 244, the valve plate 245 against the outside the valve seat 3c is pulled, and its tappet stem 246 the the valve seat 3c following cap bore 3d free or through Ridges 247 reach radially supported and freely through the Armature cylinder bore 217 goes and just before the expanded area the bore 217 ends in which the tappet plate 218 des Tappet valve 218, 219 is added.
  • This injection pump which has no piston, works in contrast to the embodiment according to FIG. 17 as follows. If the tappet valve 218, 219 from the valve seat of the armature cylinder 210 is taken, the sudden pressure build-up in the fuel takes place in space 202, 217 and 3d, so that the tappet valve 244 to Spraying against the pressure of the return spring 250 opens. Subsequently hits the plunger plate 218 after a further stroke "H" on plunger stem 246 and holds valve 244 open.
  • FIG. 19 An embodiment similar to the embodiment shown in FIG. 18 the injection pump 1 according to the invention is shown in FIG. 19 shown, the same parts again with the same reference numerals are designated.
  • the tappet stem 246 of the tappet valve 244 is made shorter and is sufficient in the rest position or starting position of the pump 1 only up to the injector-side end area of the armature cylinder bore 217. Accordingly, the return spring is 250 shortened. In addition, however, another compression spring presses 251 from the tank side against the ring 248a, which is at one end against a wall having a central bore 217d 217e supports the bore 217 in an injector side and a tank-side area divided over bore 217d communicate.
  • the spring supports this version of injection pump 1 251 the opening of the valve 244 as in the case of the embodiment 18, in which the belching through the valve plate 218 is supported, which hits the pushrod 246.
  • the Springs then also hold valve 244 in the open position, as long as the spring pressure of the spring 250 or 251 causes this.
  • an injector with multiple pumps 501 (Fig. 20), the fuel via a common delivery line 503 through the nozzle or valve 504 into the combustion chamber inject.
  • the individual pumps are preferably out of cycle operated so that the fuel pulses with a very high frequency be injected into the combustion chamber 505.
  • With a Larger number of pumps 501 can then be a quasi-continuous one Fuel supply can be achieved via a nozzle 504, the Throughput compared to traditional continuous work However, fuel supply devices are controlled much more precisely can be.
  • nozzle assembly 506 It is also possible to use several pump-nozzle units via one common nozzle assembly 506 (Fig. 21, 22) to connect.
  • a nozzle assembly 506 is a single one for each pump 501 Nozzle insert 504 provided.
  • the pumps 501 can pulse circulate so that the individual fuel pulses on the nozzle inserts 504 all the way into the combustion chamber 505 , making the flame center in the burner a circular one Movement. This clearly shows that with the device according to the invention influenced parameters conventional burner controls cannot be accessed were.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Incineration Of Waste (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (69)

  1. Brûleur à mazout pour une installation thermique comportant une chambre de combustion, dans laquelle le combustible est amené à travers un élément d'alimentation en combustible,
    caractérisé en ce que,
    ledit élément d'alimentation en combustible est un dispositif d'injection fonctionnant selon le principe d'accumulation d'énergie, muni d'une pompe (1) et d'un agencement de buses (3), ledit élément d'alimentation étant réalisé de telle manière que le combustible et/ou un élément à piston alternatif de la pompe (1) sont accélérés pendant une phase d'accélération et que, par un moyen interrompant cette phase d'accélération, l'énergie accumulée dans le combustible et/ou dans l'élément à piston est transformée en une impulsion d'injection, produisant ainsi l'émission brusque d'une quantité définie de combustible.
  2. Brûleur à mazout selon la revendication 1,
    caractérisé en ce que,
    le dispositif d'injection est réalisé de telle sorte que la quantité de carburant émise à chaque impulsion d'injection est réglable.
  3. Brûleur à mazout selon la revendication 1 ou 2,
    caractérisé en ce que,
    le dispositif d'injection est relié à une unité de commande qui régule la fréquence d'injection de telle manière qu'elle présente une distance de fréquence aussi grande que possible par rapport à la fréquence de résonance de la chambre de combustion.
  4. Brûleur à mazout selon les revendications 1 à 3,
    caractérisé par la présence d'une unité de réglage électronique équipée d'un capteur à gaz pour mesurer les gaz de combustion générés, cette unité réglant la fréquence de l'injection et/ou la quantité de l'injection en fonction du signal du capteur à gaz.
  5. Brûleur à mazout selon l'une des revendications 1 à 4,
    caractérisé par la présence de plusieurs pompes (501) qui sont reliées à une buse unique (504) par une conduite de refoulement commune (503).
  6. Brûleur à mazout selon l'une des revendications 1 à 4,
    caractérisé par la présence de plusieurs pompes (501) qui sont reliées respectivement par une conduite de refoulement (503) à, respectivement, une buse (504), lesdites buses (504) étant disposées dans un porte-buses (506) unique.
  7. Brûleur à mazout selon l'une des revendications 1 à 6,
    caractérisé en ce que la soupape d'injection fonctionne selon le principe d'accumulation d'énergie des corps solides, dans lequel un élément piston monté dans un cylindre d'une pompe à piston entraínée par un électroaimant, déplace, avant l'injection dans la zone de pompage, des quantité partielles du combustible à injecter pendant une phase d'accélération pratiquement sans résistance, alors que l'élément piston accumule de l'énergie cinétique, ce déplacement étant bloqué brutalement par des moyens d'interruption du déplacement, ce qui génère un coup de bélier dans un combustible se trouvant dans une chambre pressurisée fermée, l'énergie cinétique accumulée dans l'élément piston étant transmise directement sur le combustible se trouvant dans la chambre pressurisée et le coup de bélier étant utilisé pour injecter du combustible à travers un agencement d'injection à buses.
  8. Brûleur à mazout selon la revendication 7,
    caractérisé en ce que,
    les moyens d'interruption du déplacement et qui produisent le coup de bélier, sont disposés à l'extérieur de la zone de contact étanche aux liquides entre l'élément piston et le cylindre de la pompe à piston.
  9. Brûleur à mazout selon la revendication 7 ou 8,
    caractérisé en ce que,
    les moyens d'interruption du déplacement ou de production de la montée en pression, sont réalisés sous la forme d'un dispositif (6, 50, 70, 90, 125, 218/223) présentant un moyen de butée.
  10. Brûleur à mazout selon l'une des revendications 1 à 3,
    caractérisé en ce que,
    le moyen de butée (par exemple 37) est réalisé de manière à permettre son changement de position.
  11. Brûleur à mazout selon l'une ou plusieurs des revendications 7 à 10,
    caractérisé en ce que,
    un élément (6) d'accumulation volumique est prévu pour le déplacement du combustible pendant la phase d'accélération.
  12. Brûleur à mazout selon la revendication 11,
    caractérisé en ce qu'il présente une pompe à piston (1) à entraínement électromagnétique qui est raccordée par une conduite de refoulement (2) à un agencement d'injection (3) à buses, et la conduite de refoulement (2) dérive une conduite d'aspiration (4) qui est en liaison avec un réservoir de combustible (5), l'élément d'accumulation volumique (6) étant relié à la conduite de refoulement (2) par une conduite (7).
  13. Brûleur à mazout selon la revendication 12,
    caractérisé en ce que,
    la pompe (1) présente un carter (8) dans lequel est montée une bobine annulaire (9), et dans la région de passage, à travers cette bobine, est disposé un induit (10) conformé en cylindre et monté à l'intérieur d'un carter cylindrique qui se trouve dans la région de l'axe longitudinal central de ladite bobine (9) et est poussé au moyen d'un ressort de compression (12) dans une position de départ dans laquelle il s'applique sur le fond (11a) du carter cylindrique, un piston de refoulement (14) étant monté sur la face frontale côté buses d'injection de l'induit (10), ce piston plongeant relativement profondément dans une chambre cylindrique de refoulement du combustible (15), laquelle est disposée coaxialement par rapport au carter cylindrique et en relation de transmission avec la conduite pressurisée (2).
  14. Brûleur à mazout selon les revendications 12 et/ou 13,
    caractérisé en ce que,
    dans la conduite d'aspiration (4) est agencé un clapet anti-retour (16).
  15. Brûleur à mazout selon l'une ou plusieurs des revendications 11 à 14,
    caractérisée en ce que,
    l'élément d'accumulation (6) présente un carter (22) dans la cavité duquel est tendue une membrane (23) servant d'organe à déplacer, laquelle sépare de cette cavité une chambre placée côté conduite de pression et remplie de combustible et qui, à l'état détendu, divise la cavité en deux moitiés rendues étanches l'une à l'égard de l'autre par cette membrane, tandis que sur le côté de la membrane opposée à la conduite (7) est prévu un espace vide qui présente une paroi (22a) de forme bombée servant de moyen de butée à la membrane (23).
  16. Brûleur à mazout selon la revendication 15,
    caractérisé en ce que,
    sur le côté de la membrane (23), opposée à la conduite (7), est disposé dans l'espace vide un ressort (24) agissant sur la membrane et servant de ressort de rappel pour ladite membrane (23).
  17. Brûleur à mazout selon l'une ou plusieurs des revendications 12 à 16,
    caractérisé en ce que,
    dans la conduite pressurisée (2), entre la soupape d'injection (3) et la chambre pressurisée, est disposé, en amont des dérivations (4, 7), un clapet anti-retour (16a) qui, à l'intérieur de la chambre côté soupape d'injection, forme un espace de stockage permettant de maintenir à l'intérieur du combustible une certaine pression permanente.
  18. Brûleur à mazout selon l'une ou plusieurs des revendications 11 à 14,
    caractérisé en ce que,
    pour servir d'organe de déplacement pour l'élément d'accumulation (6), on utilise un piston d'accumulation (31) monté dans un carter cylindrique (30) et en liaison avec la conduite (7), ledit cylindre (30) rendant disponible un volume vide (33c) dans lequel le piston (31) peut être déplacé par le combustible.
  19. Brûleur à mazout selon la revendication 18,
    caractérisé en ce que,
    dans la région du volume de l'espace vide (33c) est disposé un perçage d'écoulement (32).
  20. Brûleur à mazout selon les revendications 18 et/ou 19,
    caractérisé en ce que,
    dans le volume de l'espace vide (33c) est tendu un ressort de compression (34) qui pousse le piston (31) dans sa position de repos contre une paroi (33a) du carter située du côté de la conduite pressurisée.
  21. Brûleur à mazout selon l'une ou plusieurs des revendications 18 à 20,
    caractérisé en ce que,
    dans le volume de l'espace vide (33c) est disposée une tige de butée (37) axialement réglable pour le piston (31), laquelle passe à travers la paroi du carter et est en liaison à l'extérieur dudit carter avec un moyen de réglage.
  22. Brûleur à mazout selon l'une ou plusieurs des revendications 7 à 14 et 17,
    caractérisé en ce que,
    la vanne d'arrivée (16) du combustible est réalisée sous la forme d'une vanne (50) à élément d'accumulation.
  23. Brûleur à mazout selon la revendication 22,
    caractérisé en ce que,
    la vanne (50) présente un carter cylindrique (51) dans lequel est pratiqué un perçage passant (52) qui présente une section (53) du côté conduite pressurisée et une section (53b) du côté aspiration, une chambre de vanne (54), radialement élargie, étant réalisée entre les deux qui reçoit un élément de blocage de la vanne (55) qui est constitué, en une seule pièce, d'un disque (56) de grand diamètre et d'un disque (57) de petit diamètre, le disque (57) étant disposé sur le côté de la section (53) du perçage et un ressort de rappel du corps de vanne (58) poussant l'élément de vanne à l'état de repos contre une face annulaire frontale (59) du côté de la conduite de pression de la chambre (54), cette face (59) s'appuyant d'un côté, contre le disque (56) et de l'autre, sur le fond d'un gradin annulaire (60) disposé centralement dans la face frontale (61) en regard de la face frontale (59) de la chambre (54), de telle sorte que le disque (56) peut venir en application étanche contre la face frontale (61) de la chambre (54), la section (53) du perçage étant en liaison avec la chambre (54) par des goulottes ou rainures (62) disposées dans la paroi (51) du carter, celles-ci allant avantageusement s'élargir en forme d'entonnoir en direction de la chambre (54).
  24. Brûleur à mazout selon la revendication 22,
    caractérisé par la présence d'une vanne (70) à commande électromagnétique.
  25. Brûleur à mazout selon la revendication 24,
    caractérisé en ce que,
    la vanne (70) présente, à l'intérieur d'un corps de vanne (77) une bobine annulaire (78) dans l'espace intérieur de laquelle est prévu un perçage cylindrique (74) dans lequel est monté un induit (73), lequel est en liaison avec une plaque de vanne (72) chargée par un ressort et présente, au voisinage de ladite plaque, au moins un perçage (75) s'étendant transversalement par rapport à l'extension longitudinale de l'induit, ledit induit (73) étant poussé par un ressort (76) s'appliquant contre la plaque (72) dans une position finale côté conduite pressurisée, dans laquelle le combustible est en liaison avec le combustible des chambres pressurisées (15, 2) à travers les perçages (75) et (74) et l'orifice (71) dans la conduite pressurisée.
  26. Brûleur à mazout selon la revendication 22,
    caractérisé par la présence d'un dispositif (90) intégrant une vanne d'arrivée et un élément d'accumulation, qui présente un carter (91) dans lequel est pratiqué un alésage central longitudinal (92), qui débouche sur une extrémité à travers un orifice (93a) dans la conduite pressurisée (2) et à l'autre extrémité dans une chambre cylindrique de vanne (93), tandis qu'en outre des goulottes (94) conduisent de l'alésage (92) à la chambre de vanne (93) tandis que l'élément de vanne est réalisé en deux parties et comprend un cylindre (95) monté dans la chambre (93), un piston (96) étant monté de manière coulissante dans le perçage cylindrique centrale étagé passant à travers ce cylindre (95), et des rainures axialement parallèles (97) étant réalisées dans la face enveloppante extérieure dudit cylindre (95), tandis que le cylindre (95) est poussé par un ressort (98) dans sa position de repos, dans laquelle il est appliqué par l'une de ses faces frontales sur le fond côté réservoir de la chambre (93), dans laquelle débouche une conduite d'arrivée du combustible (99) venant du réservoir, et tandis que un ressort (100) est monté dans l'alésage destiné au logement du cylindre (96) côté réservoir, ce ressort poussant le piston (96) contre le fond côté conduite de pression de la chambre de vanne (93), de telle sorte que l'alésage (92) est recouvert, tandis que dans l'espace intérieur côté réservoir du cylindre (95) se forme un espace libre (95a) pour le piston (96).
  27. Brûleur à mazout selon l'une ou plusieurs des revendications 7 à 14 et 17,
    caractérisé en ce que,
    l'élément accumulateur (6) est réalisé en une seule unité avec le piston de refoulement (14) de la pompe (1) à piston alternatif.
  28. Brûleur à mazout selon la revendication 27,
    caractérisé en ce que,
    un piston accumulateur (80) qui sert d'élément accumulateur, est pousséé par un ressort (81) contre une butée du côté conduite pressurisée à l'intérieur d'une première section (14b) de l'alésage central longitudinal axial étagé, côté conduite pressurisée, d'un alésage (14a) passant centralement à travers le piston (14) et l'induit (10), le piston (80) pénétrant dans sa position de repos par l'une de ses faces frontales dans la chambre pressurisée (15) et la section (14b) recevant le piston (80) étant prolongée à l'intérieur du piston de refoulement (14), après un gradin (14c), en direction de l'induit (10), en formant une autre section d'alésage (14d), sur le gradin (14e) de laquelle s'appuie un ressort de compression (81) qui appuie contre la face frontale côté induit.
  29. Brûleur à mazout selon la revendication 11,
    caractérisé en ce qu'une soupape hydraulique côté réservoir est logée, ensemble avec la pompe (1) et la conduite pressurisée (2), dans un carter commun (121) et constitue une soupape (122) d'admission du combustible, commandée hydrauliquement, montée dans la conduite d'arrivée du combustible, cette soupape (122) se fermant automatiquement à une vitesse de flux déterminée en vertu de l'effet Bernoulli.
  30. Brûleur à mazout selon la revendication 29,
    caractérisé en ce que,
    le combustible parvient à travers un interstice (123) dans une chambre (124) de la soupape (122), à l'intérieur de laquelle un interstice annulaire étroit subsiste entre un cône de soupape (125) et le siège correspondant, cet interstice pouvant être réglé par une conception appropriée d'un ressort (126) agissant sur le cône (125).
  31. Brûleur à mazout selon la revendication 29 et /ou 30,
    caractérisé en ce que,
    la conduite pressurisée (2) conduisant vers la buse d'injection est raccordée à la sortie d'un clapet anti-retour (127), lequel est disposé de manière monobloc à l'intérieur du carter (121) et par lequel passe le trajet suivi par le combustible pour arriver à la buse d'injection (3).
  32. Brûleur à mazout selon la revendication 31,
    caractérisé en ce que,
    le clapet anti-retour (127) présente un cône de soupape (128) qui est poussé par la précontrainte d'un ressort (129) contre un siège de soupape correspondant, ledit ressort (129) étant agencé de telle sorte que le clapet (127) soit fermé lorsque la pression s'appliquant en direction de la conduite pressurisée (2) se situe en dessous d'une valeur conduisant à une expulsion de combustible à travers la buse d'injection (3), laquelle est raccordée indirectement audit clapet (127).
  33. Brûleur à mazout selon l'une ou plusieurs des revendications 7 à 32,
    caractérisé par la présence d'un dispositif d'amortissement hydraulique pour l'élément induit (10) de la pompe à piston alternatif.
  34. Brûleur à mazout selon la revendication 33,
    caractérisé en ce que,
    le dispositif d'amortissement hydraulique est construit à la manière d'un ensemble piston-cylindre, une projection cylindrique (10a) étant réalisée centralement sur l'induit (10), cette projection s'ajustant dans la dernière section du mouvement de retour de l'induit dans un perçage cylindrique borgne (11b) pratiqué dans le fond (11a) du cylindre, des rainures (10b) qui s'étendent dans la direction longitudinale étant disposées dans ledit induit (10), ces rainures reliant à l'intérieur du cylindre de la pompe l'espace placé à l'arrière de l'induit avec celui placé à l'avant de l'induit.
  35. Brûleur à mazout selon la revendication 33,
    caractérisé en ce que,
    la chambre de pompe (11) traversée par le piston de refoulement (14) est reliée, avant le piston (10), à l'espace (11) adjacent au côté arrière de l'induit, par des perçages (10d) qui débouchent dans la région du côté arrière de l'induit dans un canal de trop-plein central (10c), une tige centrale (8a) d'un amortisseur de chocs (8b) pénétrant par une pointe conique (8c) dans la direction de l'embouchure dudit canal de trop-plein (10c).
  36. Brûleur à mazout selon la revendication 35,
    caractérisé en ce que,
    la tige centrale (8a) pénètre du côté arrière dans un trou (8d) pratiqué dans le fond (11a), lequel trou débouchant dans une chambre d'amortissement (8e), tandis que la tige (8a) s'achève à l'intérieur de cette chambre d'amortissement par une bague (8f), dont le diamètre est supérieur à celui du trou (8d), et tandis que, sur le fond de la chambre d'amortissement, s'appuie un ressort (8g) qui comprime la bague (8f), tandis qu'un canal (8h) relie la chambre d'amortissement (8e) à la chambre d'induit (11) placée du côté arrière.
  37. Brûleur à mazout selon la revendication 35,
    caractérisé en ce que,
    à l'intérieur de la tige (8a) est disposé centralement un perçage de refoulement continu (8i), à travers lequel le fluide d'amortissement peut être poussé dans le canal de trop-plein (10c).
  38. Brûleur à mazout selon la revendication 33,
    caractérisé en ce que,
    l'induit (10) lors du mouvement de retour dessert un dispositif de pompage qui, en même temps, assure la fonction d'un dispositif d'amortissement de l'induit (10).
  39. Brûleur à mazout selon la revendication 38,
    caractérisé en ce qu'une deuxième pompe (260) est raccordée au fond arrière (11a) du carter de pompe (8), cette pompe présentant un carter (261) dans la chambre de pompage (261b) duquel est disposé un piston de pompe (262) dont la tige de piston (262a) pénètre dans l'espace opérationnel (11) de l'induit (10), tandis que le piston (262) est placé sous la force d'un ressort de rappel (263) qui s'appuie sur le fond (261a) du carter au voisinage d'un échappement (264).
  40. Brûleur à mazout selon la revendication 39,
    caractérisé en ce que,
    la chambre de pompage (261b) est en liaison à travers une conduite d'arrivée (265), avec un réservoir (266), un clapet anti-retour (267) étant monté dans ladite conduite (265).
  41. Brûleur à mazout selon les revendications 33 et/ou 34,
    caractérisé en ce que,
    le perçage borgne (11b) présente un diamètre supérieur à celui de la projection cylindrique (10a) et que ladite projection (10a), ou le perçage borgne (11b), présente une bague formant lèvres d'étanchéité (10e) ou (10d), lesdites bagues d'étanchéité formant le joint de piston pour la projection (10a).
  42. Brûleur à mazout selon l'une ou plusieurs des revendications 7 à 10 et 33 à 41,
    caractérisé en ce que,
    l'induit est réalisé sous la forme d'un cylindre de pompe (210), tandis que l'espace intérieur du carter (202) est divisé par une bague (203) s'étendant radialement vers l'intérieur en un espace intérieur côté réservoir et un espace intérieur côté conduite pressurisée, et tandis que du côté conduite pressurisée, un bourrelet annulaire (204) d'un piston (205) de la pompe (1), monté de manière fixe dans cet espace intérieur dont il épouse la forme, se pose contre une arête annulaire de ladite bague (203), traverse, à une certaine distance, l'ouverture (206) de la bague (203) et pénètre dans la région côté réservoir de l'espace intérieur (202) où il pénètre dans un perçage continu (217) du cylindre induit (210).
  43. Brûleur à mazout selon la revendication 42,
    caractérisé en ce que,
    le piston (205) est traversé par un perçage continu (207) qui s'élargit dans la zone terminale côté réservoir du piston et supporte en cet endroit un clapet anti-retour (208), lequel est serré par un ressort hélicoïdal (209) contre un siège de clapet (209a), en direction du côté réservoir pour obtenir la position de fermeture.
  44. Brûleur à mazout selon la revendication 42 et/ou 43,
    caractérisé en ce que,
    sur la partie du piston (205) se trouvant dans l'espace intérieur côté réservoir de l'espace intérieur (202) est monté, de manière ajustée géométriquement et coulissant, le cylindre (210) de la pompe dont une face frontale annulaire (214) est poussée par un ressort hélicoïdal (211) s'appuyant à une extrémité sur la bague (203) et à l'autre extrémité sur un gradin annulaire (212) du cylindre (210), contre un gradin annulaire (213) situé dans l'espace intérieur (202), tandis qu'un raccord de soupape (215) surmontant la face annulaire frontale (214) pénètre, avec une certaine distance radiale, légèrement dans l'espace intérieur (202) rétréci radialement en cet endroit, et tandis que la face annulaire frontale (214) côté conduite pressurisée du cylindre (210) est disposée à une certaine distance de la bague (203), ce qui a pour effet de créer un espace de mobilité pour le cylindre (210).
  45. Brûleur à mazout selon la revendication 44,
    caractérisé en ce que,
    le cylindre (210) monté de manière géométriquement ajustée sur la paroi intérieure de l'espace intérieur (202) présente, dans sa surface enveloppante, des rainures longitudinales (216) axialement parallèles, ouvertes du côté frontal, et en ce que l'alésage (217) traversant le cylindre de pompe (210) et recevant le piston (205) supporte, du côté réservoir, une soupape poussoir située en amont du piston (205), dont le plateau (218) est disposé à une certaine distance de la surface annulaire frontale du piston (205) dans un court élargissement de l'alésage et dont la tige (219) traverse l'alésage rétréci (217a) dans le raccord de soupape (215), en s'appuyant contre la paroi intérieure de cet alésage (217a), et pénètre dans l'espace intérieur rétréci (202a).
  46. Brûleur à mazout selon la revendication 45,
    caractérisé en ce que,
    sur l'extrémité libre de la tige poussoir (219) est fixé un plateau (220) qui présente des trous (221), ladite tige poussoir (219) débordant encore légèrement au-delà dudit plateau (220) et butant contre la face de fond (222) côté réservoir de l'espace intérieur (202a), tandis que la longueur de la tige poussoir (219) ayant été choisie telle que le plateau de poussoir (218) se soulève de son siège (223) dans l'alésage rétréci (217a), formant ainsi un interstice déterminé "X".
  47. Brûleur à mazout selon la revendication 46,
    caractérisé en ce qu'un ressort hélicoïdal (224) stabilise la position de la soupape à poussoir dans la position de repos de la pompe, du fait que le ressort (224) s'appuie par une extrémité sur la face annulaire frontale (214) du cylindre (210) et par l'autre extrémité contre le plateau (220).
  48. Brûleur à mazout selon l'une ou plusieurs des revendications 42 à 47,
    caractérisé en ce que,
    des perçages axialement parallèles (225) s'étendent de la face de fond (222) vers la paroi de fond et débouchent dans une chambre de soupape axiale (226), dans laquelle est disposé une tête de soupape (229) poussée par un ressort hélicoïdal (228) en direction du réservoir contre un siège de soupape (227), la tête (229) présentant des gorges (230) pouvant être recouvertes périphériquement par le siège de soupape (227) de telle manière que la soupape peut être ouverte par une pression du côté du raccord de réservoir à l'encontre de la charge du ressort (228) et créant ainsi un passage allant de la chambre de soupape (226) vers les perçages (225).
  49. Brûleur à mazout selon la revendication 42,
    caractérisé en ce que,
    le piston (205) est réalise en une seule pièce avec la paroi frontale (200d) du carter (200), la soupape de pression permanente (208, 209) étant montée côté conduite de pression en amont du piston (205) à l'intérieur d'un raccord tubulaire (208a) et recouvrant le débouché côté conduite pressurisée du perçage (207) qui traverse le piston (205).
  50. Brûleur à mazout selon la revendication 49,
    caractérisé en ce que,
    la tige poussoir (219) est relativement courte et ne peut déborder au-delà de la face annulaire frontale côté réservoir (214) du cylindre (210) que de la valeur du jeu de la soupape.
  51. Brûleur à mazout selon la revendication 50,
    caractérisé en ce que,
    la face annulaire frontale (214) bute, dans la région de la paroi frontale (200c), contre un bloc en matière plastique (231), monté en cet endroit, qui présente des perçages passants (232) qui débouchent périphériquement dans des rainures (233), lesquelles sont en liaison avec l'espace intérieur (202) côté réservoir, tandis que de cet espace (202) côté réservoir des perçages (234) conduisent vers une région élargie de l'alésage (217) pratiqué dans le cylindre (210) et tandis que des perçages (232) débouchent dans la chambre de soupape axiale (226) conduisant vers le réservoir et logée dans un raccord tubulaire (226a).
  52. Brûleur à mazout selon la revendication 51,
    caractérisé en ce que,
    l'élargissement de l'alésage (217), dans lequel est logé le plateau de poussoir (218), forme du côté conduite pressurisée un gradin annulaire (235) qui se trouve en position de repos de la soupape à une faible distance seulement devant le plateau de poussoir (218) et contre lequel ce dernier vient buter lorsque le poussoir, sous l'effet de l'inertie, se soulève du siège de soupape lors du mouvement de retour du cylindre (210) et/ou lorsque la soupape était repoussée brusquement par le bloc en matière plastique (231) lors du mouvement de retour du cylindre (210).
  53. Brûleur à mazout selon la revendication 52,
    caractérisé en ce que,
    dans la face frontale du gradin annulaire (235) sont pratiqués des évidements (235a) qui assurent un passage sans obstacle du combustible.
  54. Brûleur à mazout selon l'une ou plusieurs des revendications 51 à 53,
    caractérisé en ce que,
    la face annulaire frontale (214) est disposée à une faible distance de la surface du bloc en matière plastique (231).
  55. Brûleur à mazout selon la revendication 54,
    caractérisé en ce que,
    sur la surface annulaire frontale (214) sont disposées des arêtes de renfort en saillie (214a).
  56. Brûleur à mazout selon l'une ou plusieurs des revendications 42 à 55,
    caractérisé par la présence d'un dispositif d'amortissement à induit dans la zone terminale libre de la tige poussoir (219), une bague collier (219a) étant disposée en cet endroit qui entoure latéralement en partie la face annulaire frontale (214) et qui peut venir s'appliquer contre celle-ci, et tandis que dans la surface du bloc en matière plastique (231) est pratiqué un évidement (231a) qui correspond à cette bague collier (219a), laquelle s'ajuste sensiblement géométriquement dans cet évidement.
  57. Brûleur à mazout selon la revendication 56,
    caractérisé en ce que,
    l'épaisseur de la bague collier (219a) est légèrement supérieure à la profondeur de l'évidement (231a).
  58. Brûleur à mazout selon l'une ou plusieurs des revendications 42 à 57,
    caractérisé en ce que,
    dans la paroi frontale (200d) côté conduite de pression est disposé un perçage (234) qui conduit de l'espace intérieur (202) côté conduite de pression vers l'extérieur et sur lequel est posé avantageusement du côté extérieur un raccord (237) muni d'un perçage passant (238), du combustible pouvant être pompé à travers ce perçage (236) et le raccord (237) par le cylindre induit (210), pendant la phase de démarrage de la pompe (1) ou du brûleur, voire de manière permanente.
  59. Brûleur à mazout selon l'une ou plusieurs des revendications 41 à 58,
    caractérisé en ce que,
    sur la paroi intérieure de l'espace intérieur (202) côté conduite de pression est disposé un ressort de compression (238a) s'appuyant contre la paroi frontale (200b), contre lequel vient buter une face annulaire frontale (239) du cylindre induit (210) pendant l'accélération de ce cylindre, ce qui a pour effet de comprimer ce ressort.
  60. Brûleur à mazout selon l'une ou plusieurs des revendications 42 à 59,
    caractérisé en ce que,
    le cylindre (210) passe dans l'espace intérieur (202) de manière étanche au liquide sous la forme d'un élément d'induit du genre piston.
  61. Brûleur à mazout selon la revendication 60,
    caractérisé en ce qu'un piston (205a), monté partiellement à l'intérieur de l'alésage (217), est monté de manière axialement mobile et fait partie de l'agencement d'injection à buses (3).
  62. Brûleur à mazout selon la revendication 61,
    caractérisé en ce que l'agencement (3) présente un capuchon de soupape (3b) qui est vissé dans la paroi frontale (200d) du carter (200) en s'engageant dans l'espace intérieur (202) côté soupape à injection, le piston (205a) recouvrant dans sa position de repos le perçage des buses d'injection (3d) par une surface frontale (205b) de diamètre réduit, et la surface à diamètre réduit (205b) étant prolongée par un tronc de cône (205c) pour former ensuite la partie cylindrique du piston (205a).
  63. Brûleur à mazout selon la revendication 62,
    caractérisé en ce que,
    le piston (205a) est poussé dans l'alésage (217) par un ressort de compression (240) contre le perçage (3d) de la buse d'injection, le ressort de compression (240) s'appuyant par son autre extrémité contre une paroi intermédiaire (241) disposée dans l'alésage (217) et divisant ledit alésage (217) en une zone côté buse à injection et une zone côté réservoir.
  64. Brûleur à mazout selon la revendication 63,
    caractérisé en ce qu'au moins un perçage (242) conduit de la paroi annulaire frontale (212), à travers le cylindre induit (210), dans l'espace élargi de la zone côté réservoir de l'alésage (217), espace élargi dans lequel est logé le plateau de poussoir (218), et en ce qu'un perçage (243) passe à travers le cylindre induit (210) entre la zone côté injection de l'alésage (217) vers l'espace intérieur côté réservoir (202), la région centrale du cylindre induit (210) étant montée de manière géométriquement ajustée et pratiquement étanche au liquide sur la paroi intérieure de l'espace intérieur (202).
  65. Brûleur à mazout selon la revendication 64,
    caractérisé en ce que,
    le cylindre induit (210) présente dans la zone côté réservoir de l'espace intérieur (202), des rainures, les bords de ces rainures s'appliquant contre la paroi intérieure de l'espace intérieur (202) pour y former des guidages pour le cylindre induit (210).
  66. Brûleur à mazout selon l'une ou plusieurs des revendications 42 à 60,
    caractérisé en ce que,
    la buse d'injection (3) est logée directement dans la paroi frontale (200d) du carter (200) et présente un capuchon (3b) muni d'un siège de soupape (3c) pour une soupape poussoir (244), dont la tête (245) est tirée de l'extérieur contre le siège de soupape (3c) et dont la tige poussoir (246) traverse le perçage (3d) pratiqué dans le capuchon et faisant suite au siège de soupape (3c), ou bien librement ou bien de manière radialement renforcé par des nervures (247) et traverse librement l'alésage (217) et s'achève à courte distance avant la région élargie dudit alésage (217), dans lequel le plateau de poussoir (218) de la soupape poussoir (218, 219) est logé, tandis qu'à l'extrémité libre de la tige poussoir (246) est fixée une bague (248a) présentant des trous ou évidements radiaux (248) contre laquelle s'appuie un ressort de compression (250) du côté soupape à injection, ce ressort s'appliquant à l'autre extrémité à la paroi frontale (200d) du carter (200) ou sur le capuchon (3b), tandis que le cylindre induit (210) ne présente que l'alésage (217a) et aucune rainure radiale mais s'applique de manière géométriquement ajustée et étanche au liquide contre la paroi intérieure de l'espace intérieur (202) et le plateau de poussoir (218) venant buter, après une course déterminée, sur la tige poussoir (246) lors du mouvement de pompage.
  67. Brûleur à mazout selon la revendication 66,
    caractérisé en ce que,
    la tige poussoir (246) de la soupape poussoir (244) est plus courte et n'arrive, en position de repos de la pompe (1), que dans la zone terminale côté soupape d'injection de l'alésage (217), tandis qu'un autre ressort de compression (251) exerce une compression du côté réservoir contre la bague (248a), ce ressort s'appuyant par une extrémité contre une paroi (217e) présentant un perçage central (217d), cette paroi divisant l'alésage (217) en une zone côté soupape à injection et une zone côté réservoir, ces deux zones étant reliées mutuellement par le perçage (217d).
  68. Brûleur à mazout selon l'une des revendications 1 à 67,
    caractérisé par la présence d'un dispositif retardant le flux de combustible, dont l'action transforme instantanément l'énergie cinétique du combustible accélérée en une onde de choc qui injecte le combustible à travers la buse d'injection.
  69. Brûleur à mazout selon la revendication 68,
    caractérisé par la présence d'une installation de commande électronique commune (608) pour la pompe (602) et le dispositif retardateur (606) à commande électrique.
EP95924243A 1994-06-16 1995-06-14 Bruleur a mazout Expired - Lifetime EP0764254B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4421145A DE4421145A1 (de) 1994-06-16 1994-06-16 Ölbrenner
DE4421145 1994-06-16
PCT/EP1995/002317 WO1995034786A1 (fr) 1994-06-16 1995-06-14 Bruleur a mazout

Publications (2)

Publication Number Publication Date
EP0764254A1 EP0764254A1 (fr) 1997-03-26
EP0764254B1 true EP0764254B1 (fr) 1998-09-02

Family

ID=6520795

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95924243A Expired - Lifetime EP0764254B1 (fr) 1994-06-16 1995-06-14 Bruleur a mazout

Country Status (8)

Country Link
US (1) US6004127A (fr)
EP (1) EP0764254B1 (fr)
JP (1) JP2935576B2 (fr)
AT (1) ATE170615T1 (fr)
AU (1) AU690300B2 (fr)
CA (1) CA2187275A1 (fr)
DE (2) DE4421145A1 (fr)
WO (1) WO1995034786A1 (fr)

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JP5067110B2 (ja) * 2007-10-17 2012-11-07 マックス株式会社 ガス燃焼式打込み工具
US8052418B2 (en) 2008-09-05 2011-11-08 Energy Efficiency Solutions, Llc Oil burning system
US8464742B2 (en) * 2010-02-11 2013-06-18 Honeywell International Inc. Injection or other system with anti-thermal lockdown mechanism and related method
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US8523560B2 (en) 2010-04-09 2013-09-03 Honeywell International Inc. Spark detection in a fuel fired appliance
US10208954B2 (en) 2013-01-11 2019-02-19 Ademco Inc. Method and system for controlling an ignition sequence for an intermittent flame-powered pilot combustion system
US9494320B2 (en) 2013-01-11 2016-11-15 Honeywell International Inc. Method and system for starting an intermittent flame-powered pilot combustion system
CA2857775C (fr) * 2013-07-25 2020-06-02 Yutaka Giken Co., Ltd. Dispositif d'echange de chaleur
US11236930B2 (en) 2018-05-01 2022-02-01 Ademco Inc. Method and system for controlling an intermittent pilot water heater system
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Also Published As

Publication number Publication date
DE4421145A1 (de) 1995-12-21
CA2187275A1 (fr) 1995-12-21
AU2883295A (en) 1996-01-05
WO1995034786A1 (fr) 1995-12-21
US6004127A (en) 1999-12-21
JPH09512896A (ja) 1997-12-22
EP0764254A1 (fr) 1997-03-26
AU690300B2 (en) 1998-04-23
ATE170615T1 (de) 1998-09-15
DE59503445D1 (de) 1998-10-08
JP2935576B2 (ja) 1999-08-16

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