EP0263340A2 - Brûleur à huile - Google Patents

Brûleur à huile Download PDF

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Publication number
EP0263340A2
EP0263340A2 EP87113635A EP87113635A EP0263340A2 EP 0263340 A2 EP0263340 A2 EP 0263340A2 EP 87113635 A EP87113635 A EP 87113635A EP 87113635 A EP87113635 A EP 87113635A EP 0263340 A2 EP0263340 A2 EP 0263340A2
Authority
EP
European Patent Office
Prior art keywords
oil
valve
piston
shut
pressure chamber
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.)
Granted
Application number
EP87113635A
Other languages
German (de)
English (en)
Other versions
EP0263340A3 (en
EP0263340B1 (fr
Inventor
Werke Carry Gross Gmbh Abig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Abig Werke Carry Gross & Co KG GmbH
Original Assignee
Abig Werke Carry Gross & Co KG GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Abig Werke Carry Gross & Co KG GmbH filed Critical Abig Werke Carry Gross & Co KG GmbH
Priority to AT87113635T priority Critical patent/ATE60422T1/de
Publication of EP0263340A2 publication Critical patent/EP0263340A2/fr
Publication of EP0263340A3 publication Critical patent/EP0263340A3/de
Application granted granted Critical
Publication of EP0263340B1 publication Critical patent/EP0263340B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F23K5/14—Details thereof
    • F23K5/18—Cleaning or purging devices, e.g. filters
    • 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
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/02—Liquid fuel
    • F23K5/14—Details thereof
    • F23K5/147—Valves

Definitions

  • the invention relates to an oil burner according to the preamble of claim 1.
  • Such an oil burner has an oil pump.
  • This oil pump can be connected to an oil tank with an oil inlet and has a pressure relief valve which directs the excess oil back to the tank through an oil drain.
  • Oil is pumped from the pressure relief valve to a burner nozzle.
  • a controllable shut-off valve is arranged in the connecting line between the burner nozzle and the pressure relief valve, which can generally be controlled by means of an electromagnet. This shut-off valve closes or opens when the pump motor is switched off or when the nominal speed of the pump motor is reached.
  • a heating cartridge of about 10 mm in diameter and about 100 mm in length is arranged in the nozzle rod assembly, which heats the oil directly in front of the nozzle.
  • the temperature is brought to about 90 ° C at the low throughputs mentioned above.
  • a thermostat which represents the cold oil lock for the burner, now switches the burner on when the above-mentioned oil temperature is reached.
  • the oil temperature decreases with increasing oil output, so that the oil may only have a temperature of 30 ° C to 40 ° C with an oil operation of 3kg / h. This slight increase in the oil temperature to a constant level is enough to operate the burner safely.
  • a disadvantage of this known suction device is that too much oil is sucked out of the pipe system; this leads to the fact that after the shut-off valve is opened again, the oil jet that emerges from the burner nozzle builds up only gradually, so that the ignition of the oil jet starts late and in turn burned oil in the vicinity of the Can form burner nozzle deposits.
  • the invention has for its object to further develop the known oil burner mentioned at the outset such that on the one hand dripping of the burner nozzle is reliably prevented, while on the other hand it should be ensured that the oil jet emerging from the burner nozzle when the burner is restarted Oil pump builds up faster than was previously the case.
  • the oil suction device has a displacement piston which is sealingly movable in a cylinder and which is located in an interior in its first end position, but leaves it in its second end position.
  • the interior is connected to the end pipe.
  • this displacement piston can in turn be moved from the first to the second end position by an electromagnet, the oil in the end line being sucked into the interior.
  • the interior is dimensioned such that so much oil is sucked out of the end line located between the interior and the burner nozzle that oil seepage from the nozzle opening is reliably prevented.
  • the interior is completely filled with oil, and when the shut-off valve is opened, the piston can be moved into the interior into its second end position at the same time by an electromagnetic drive, so that the oil located in the interior is displaced back into the end line.
  • the pressure begins, the end line does not have to fill up, but the pressure hits the end line that is already filled with oil and propagates in the oil filling, so that a particularly steep pressure rise occurs at the burner nozzle and the escaping oil jet builds up abruptly.
  • the interior and piston can also be designed to be relatively small, so that the piston responds with little inertia because of its low mass.
  • the required control connection between the shut-off valve and the piston can have an electromagnet, which is energized together with the shut-off valve and moves the piston to enlarge or reduce the interior space.
  • a pressure chamber is thus provided in the connection between the shut-off valve and the end line, with which the end of the piston facing away from the interior is connected.
  • This pressure chamber is in turn connected to a return device, which can be closed by a valve controlled by the oil pressure or otherwise. If the pressure in the pressure chamber drops when the shut-off valve is closed, the piston can fall into the interior of the pressure chamber by gravity or suction, increasing the interior space. The oil from the end pipe now fills this interior.
  • the piston is urged towards the pressure chamber by a spring; by appropriate arrangement of the return line e.g. Provision is therefore made at the top of the pressure chamber so that only that amount of oil is displaced from the pressure chamber which corresponds to the part of the piston penetrating into it. It is thus reliably prevented that too much oil is withdrawn from the line system when the oil pump is switched off.
  • the piston itself is according to a further preferred embodiment of the invention hidden as a valve slide, which in its second end position, in which it releases the interior and in which it sucks in the oil from the end line, simultaneously shuts off the connection between the latter and the pressure chamber and thus also the shut-off valve.
  • the piston moves from its second end position into the first end position, then it presses the oil from the interior into the end line and then opens the connection between the latter and the pressure chamber, so that when the line system is pressurized by the oil pump, almost the entire pipe system is already filled with oil.
  • a shut-off device is arranged between the pressure chamber and the return line.
  • a shut-off valve can consist of an arrangement of several valves, or of a controllable valve slide which, depending on the operating state, assumes a position in which it connects the pressure chamber and the return line, by means of a servomotor, for example a pressure adjusting device or an electromagnet opens or closes.
  • a particularly simple and thus also advantageous embodiment of the invention uses a shut-off valve with a valve body which can be moved between two end positions against a valve seat in order to shut off the connection in each of these end positions. If the valve body is between the two end positions, oil can flow around it. This valve spool is pressed by a valve spring against the valve seat facing the pressure chamber.
  • valve spring The strength of the valve spring is set such that its force is overcome by it when the operating chamber is at normal operating pressure and the valve body is pressed against that valve seat. which faces away from the pressure chamber. If the shut-off valve closes so that the pressure in the pressure chamber collapses, the valve spring presses the valve body away from the latter valve seat. However, there is still a residual pressure in the pressure chamber, since the piston, when it has blocked the connection between the pressure chamber and the end line in its action as a gate valve, is pressed even further by its piston spring against the pressure chamber and thus seeks the oil in it to displace. This is also possible because this oil can flow around the valve body which is in a central position.
  • the invention not only succeeds in sucking off the oil in the end line when the oil pump is switched off, but by pumping this oil back into the end line when the oil pump is started up again, a rapid and steep pressure increase at the burner nozzle is ensured and thus the formation of deposits in the Circumference of the burner nozzle is further reduced.
  • a feed pump 1 is operated by an electric motor, not shown in the drawing, and has a pressure relief valve, not shown in the drawing, which ensures that, in spite of the occurrence of an excessive delivery quantity and an excessively high delivery pressure, this pressure is not passed on, but the excess Oil is derived.
  • the oil is fed to the pump via an oil inlet 2; the excess oil is conveyed back through an oil drain 3 to the storage tank to which the oil feed 2 is also connected.
  • a pump line 4 is also connected to the pump, as is a return line 27 which, as indicated by dashed lines, is connected to the oil drain 3.
  • the delivery pump 1 In the delivery line 4, in which there is constant pressure during operation due to the action of the pressure relief valve, the delivery pump 1 is a shut-off valve 5 downstream, which can be actuated for example by an electromagnet.
  • An oil suction device 6 is connected to the shut-off valve 5.
  • This oil suction device 6 has a block 7, with an inlet 8, to which the delivery line 4, which comes from the shut-off valve 15, is connected.
  • the inlet 8 opens into a pressure chamber 9 in the interior of the block 7. This is formed by the part of a central, multi-step through hole.
  • a pressure relief valve 10 is screwed, a shut-off valve 10 is screwed, which is connected to the return line 27.
  • the pressure chamber 9 widens downward to form a support shoulder and then narrows to form a cylinder bore 11. This cylinder bore 11 is sealed at the bottom by a threaded plug 12.
  • the cylinder bore 11 has an annular groove 13 approximately in the middle of its longitudinal extent, into which a bore, which forms an oil outlet opening 14 and opens tangentially to the central bore, opens.
  • An enlarged section 15 is arranged between the cylinder bore 11 and the thread receiving the plug 12.
  • annular seal 16 is arranged at the end of the cylinder bore 11 facing the pressure chamber 9.
  • a piston 17 is slidably guided, which penetrates the ring seal 16 and is sealingly guided therein.
  • this piston lies with its transverse surface facing the pressure chamber 9 against that shoulder which is formed in the pressure chamber 9.
  • the stopper 12 has a recess which faces the piston 17 and has a slightly larger diameter than this. In the operating position shown in FIG. 1, the piston 17 lies with its end facing the stopper 12 in the aforementioned rotation.
  • the plug 12 and the piston 17 each have a central bore in which a piston spring 18 is inserted.
  • This piston spring 18 is designed as a helical compression spring.
  • the plug 12 is screwed into the central bore of the block 7 only to such an extent that its inner end does not lie against the shoulder which forms the transition between the cylinder bore 11 and the enlarged section 15.
  • a connecting bore 19 is arranged between the oil outlet opening 14 and the enlarged section 15, which creates a connection between the oil outlet opening 8 and the interior 20 of the cylinder bore 11.
  • An end line 21, which opens into a burner nozzle 22, is connected to the oil outlet opening 8.
  • the shut-off valve 10 has a central through-bore which runs coaxially to that of the block 7. This through hole widens from bottom to top to form a transverse shoulder 23, which forms a first valve seat for a valve body 24, which is arranged in an enlarged section of the central bore of the closing valve 10.
  • a second valve seat 25 is formed in the bore receiving this, which e.g. consists of a plastic ring, which is pressed into an annular groove pierced into the bore.
  • An oil-permeable spring support is arranged above the second valve seat 25; the valve body 24 has a blind bore facing it.
  • the blind bore receives a valve spring 26, which is designed as a compression coil spring and presses the valve body 24 downward against the first valve seat 23.
  • the feed pump 1 sucks in oil from a tank (not shown) via the oil inlet 2, which is fed into the delivery line 4 at constant pressure and flows through the shut-off valve 5 which is open in this operating state.
  • the oil passes through the inlet 8 of the block 7 into the pressure chamber 9, in which the full operating pressure is also established. Due to this relatively high pressure, the valve slide 24 is pressed upward against the second valve slide 25, while the piston 17 is pressed downward into its first end position, in which it rests with its lower end in the recess of the stopper 12.
  • the upper edge of the piston 17 is located at the level of the center of the annular groove 13.
  • the oil pressure also propagates through the connecting bore 19 into the enlarged section 15, but cannot act on the piston 17 from below, since, as mentioned above, the piston 17 is seated on the bottom of the recess in the stopper 12.
  • the operating state shown in FIG. 2 is established: in this case the power supply to the electric motor driving the feed pump 1 is first interrupted; this current also keeps the shut-off valve 5 open, so that it is also closed by spring force. From this point on, any pressure delivery to the inlet 8 is omitted. Since the pressure chamber 9 is open towards the end line 21, the pressure prevailing in it drops so that the piston spring 18 is able to push the piston 17 upwards into the pressure chamber 9. Here, the piston 17 dips into the ring seal 16 and thus interrupts the connection between the pressure chamber 9 and the end line 21.
  • valve body 24 With the drop in pressure in the pressure chamber 9, the valve body 24 has also moved into its lower, first end position due to the action of the valve spring 26, in which it bears against the valve seat 23.
  • the pressure chamber 9 is completely closed again and the pressure prevailing in it increases as a result of the action of the piston spring 18, which presses the piston upward into the pressure chamber 9.
  • the force of the compression spring 18 is now matched to that of the valve spring 26 so that the valve body 24 lifts off slightly, but does not come into contact with the upper, second valve seat 25.
  • the oil in the pressure chamber 9 is thus displaced by the piston 17, flows around the valve body 24 and passes through the return line 27 and the pump 1 into its oil outlet 3.

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)
  • Details Of Reciprocating Pumps (AREA)
EP87113635A 1986-10-08 1987-09-17 Brûleur à huile Expired - Lifetime EP0263340B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87113635T ATE60422T1 (de) 1986-10-08 1987-09-17 Oelbrenner.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863634345 DE3634345A1 (de) 1986-10-08 1986-10-08 Oelbrenner
DE3634345 1986-10-08

Publications (3)

Publication Number Publication Date
EP0263340A2 true EP0263340A2 (fr) 1988-04-13
EP0263340A3 EP0263340A3 (en) 1989-04-26
EP0263340B1 EP0263340B1 (fr) 1991-01-23

Family

ID=6311346

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87113635A Expired - Lifetime EP0263340B1 (fr) 1986-10-08 1987-09-17 Brûleur à huile

Country Status (3)

Country Link
EP (1) EP0263340B1 (fr)
AT (1) ATE60422T1 (fr)
DE (2) DE3634345A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0667491A2 (fr) * 1994-02-12 1995-08-16 Suntec Industries France (Sa) Dispositif d'alimentation en fuel pour brûleur à fuel
WO2022238577A3 (fr) * 2021-05-14 2023-01-05 Webasto SE Dispositif de chauffage mobile doté d'une conduite d'alimentation en combustible et procédé de fonctionnement d'un dispositif de chauffage mobile

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4020005C1 (fr) * 1990-06-24 1991-12-19 Danfoss A/S, Nordborg, Dk
DE4310837C1 (de) * 1993-04-02 1994-02-03 Bayerische Motoren Werke Ag Brennstoffversorgungssystem eines Brennkraftmaschinen-Abgasbrenners
DE19903831C2 (de) * 1999-02-01 2001-03-08 Satronic Ag System aus einer Ölpumpe und einem Ventil für Ölbrenner

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2468960A (en) * 1944-05-10 1949-05-03 John S Case Valve device
US2685919A (en) * 1951-08-24 1954-08-10 Ray Oil Burner Co Retracting system for oil burners
US2686562A (en) * 1950-01-20 1954-08-17 Jet Heet Inc Liquid fuel burner system with spray nozzle evacuator
US2741301A (en) * 1952-04-03 1956-04-10 Fluid Systems Inc Fuel tube drain devices
GB861087A (en) * 1958-06-28 1961-02-15 Bosch Gmbh Robert Improvements in or relating to fuel oil feed systems for furnaces
US3987810A (en) * 1970-12-07 1976-10-26 Bjoerklund Curt Arnold Burner scavenging valve
DE2735764A1 (de) * 1976-08-31 1978-03-09 Curt Arnold Bjoerklund Ventil
FR2477266A1 (fr) * 1980-02-28 1981-09-04 Sundstrand Corp Ensemble a bruleur a combustible liquide
FR2499213A1 (fr) * 1981-01-31 1982-08-06 Vaillant Sarl Bruleur a mazout

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1237249B (de) * 1959-09-07 1967-03-23 Josef Renner Vorrichtung zum Verhindern des Nachtropfens von OEl-Zerstaeuberbrennern
DE1401774A1 (de) * 1962-03-20 1968-10-10 Danfoss As Verfahren und Vorrichtung zum Entfernen der Fluessigkeit aus der hinter dem Absperrventil gelegenen Austrittsleitung einer Druckfluessigkeits-Foerderanlage
DE3308208A1 (de) * 1983-03-08 1984-09-13 Abig Werke Carry Gross GmbH & Co KG, 7770 Überlingen Oelbrenner

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2468960A (en) * 1944-05-10 1949-05-03 John S Case Valve device
US2686562A (en) * 1950-01-20 1954-08-17 Jet Heet Inc Liquid fuel burner system with spray nozzle evacuator
US2685919A (en) * 1951-08-24 1954-08-10 Ray Oil Burner Co Retracting system for oil burners
US2741301A (en) * 1952-04-03 1956-04-10 Fluid Systems Inc Fuel tube drain devices
GB861087A (en) * 1958-06-28 1961-02-15 Bosch Gmbh Robert Improvements in or relating to fuel oil feed systems for furnaces
US3987810A (en) * 1970-12-07 1976-10-26 Bjoerklund Curt Arnold Burner scavenging valve
DE2735764A1 (de) * 1976-08-31 1978-03-09 Curt Arnold Bjoerklund Ventil
FR2477266A1 (fr) * 1980-02-28 1981-09-04 Sundstrand Corp Ensemble a bruleur a combustible liquide
FR2499213A1 (fr) * 1981-01-31 1982-08-06 Vaillant Sarl Bruleur a mazout

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0667491A2 (fr) * 1994-02-12 1995-08-16 Suntec Industries France (Sa) Dispositif d'alimentation en fuel pour brûleur à fuel
DE4404517A1 (de) * 1994-02-12 1995-08-17 Suntec Ind France Sa Ölversorgung für einen Ölbrenner
EP0667491A3 (fr) * 1994-02-12 1996-03-27 Suntec Ind France Sa Dispositif d'alimentation en fuel pour brûleur à fuel.
DE4404517C2 (de) * 1994-02-12 1999-07-29 Suntec Ind France Sa Hydraulische Schaltung für einen Ölbrenner
WO2022238577A3 (fr) * 2021-05-14 2023-01-05 Webasto SE Dispositif de chauffage mobile doté d'une conduite d'alimentation en combustible et procédé de fonctionnement d'un dispositif de chauffage mobile

Also Published As

Publication number Publication date
DE3634345A1 (de) 1988-04-21
ATE60422T1 (de) 1991-02-15
DE3634345C2 (fr) 1990-02-22
EP0263340A3 (en) 1989-04-26
EP0263340B1 (fr) 1991-01-23
DE3767640D1 (de) 1991-02-28

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