US3587977A - Fuel injection nozzle - Google Patents

Fuel injection nozzle Download PDF

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Publication number
US3587977A
US3587977A US866244A US3587977DA US3587977A US 3587977 A US3587977 A US 3587977A US 866244 A US866244 A US 866244A US 3587977D A US3587977D A US 3587977DA US 3587977 A US3587977 A US 3587977A
Authority
US
United States
Prior art keywords
valve plate
fuel
nozzle
spring
valve
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
US866244A
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English (en)
Inventor
Paul Fussner
Gunter Hirsch
Dieter Vogt
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Priority claimed from DE19681806674 external-priority patent/DE1806674C3/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3587977A publication Critical patent/US3587977A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/02—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 of valveless type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
    • F23D11/26—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed
    • F23D11/28—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed with flow-back of fuel at the burner, e.g. using by-pass

Definitions

  • Greigg ABSTRACT A fuel injection nozzle including a turbulence chamber from which one part of the fuel admitted to the nozzle is injected into a combustion zone through a nozzle opening, while the other part of the fuel is returned from the turbulence chamber to a fuel tank through a return channel provided in the nonle and controlled by a disc valve; the valve plate of said disc valve is urged into a closed position by an adjustable closing spring engaging the valve plate eccentrically, said valve plate is urged into an open position by the pressure prevailing in said turbulence chamber. When said pressure overcomes the force of said spring, the valve plate is unseated by a tilting motion made possible by said offcenter engagement.
  • This invention relates to a fuel injection nozzle wherein the injected fuel quantities are changed by varying the bypassing fuel quantities taken out from the fuel flow introduced into the I nozzle and wherein the nozzle is provided with a turbulence chamber in which the fuel supply channels merge tangentially and with-which a return channel communicates. In the latter there is disposed a closing element which is opened by the pressure prevailing in the turbulence chamber, overcoming the force of a closing spring which may be adjusted for varying the fuel quantities.
  • Fuel injection nozzles of this type find application in particular in oil burning apparatus using heating oil as fuel which is delivered by a pump under constant pressure to the injection nozzle. The latter injects one part of the fuel into the combustion zone and returns the other part through a return conduit to the fuel tank or to the suction side of said pump. The quantities to be injected are determined by the pressure prevailing in the turbulence chamber.
  • the supply of heating oil to the injection nozzle is interrupted by the stoppage of the pump and the aforenoted closing element, under the effect of the closing spring, shuts off the return channel.
  • the closing element reopens which, because of the sudden flow of the heating oil, occurs in an impactlike manner.
  • the closing element is thus displaced against the force of the closing spring and thereafter assumes a position in which it provides a certain flow passage section determined by the equilibrium of a force exerted to a face of the closing element by the fuel pressure in the opening direction and the force of the closing spring exerted in the closing direction.
  • the said flow passage section determines the fuel injection control pressure in the turbulence chamber.
  • the closing element is formed as a disc valve, the valve plate of which is loaded offcenter by the closing spring.
  • the valve plate is tilted about an edge portion thereof.
  • the force of the closing spring may be varied by an adjusting means threadedly disposed in the return channel.
  • a sleeve bolt 2 threadedly received in a bore 1' clamps an insert 3 against an inner wall portion of nozzle body 1.
  • a turbulence chamber generally indicated at 4 which is formed of a cylindrical cavity 3' provided in the terminal face of insert 3 and an adjoining conical space 1" defined by wallportions of nozzle body I.
  • the conical space 1" continues in a nozzle opening 5.
  • the cylindrical cavity 3' of the turbulence chamber 4 communicates through an axial bore 6 of the insert 3 with a fuel return channel formed of the inner bore 7 of sleeve bolt 2.
  • a plurality of fuelsupply channels 8 (only one is shown) merge tangentially into the turbulence chamber 4.
  • the insert 3 has a sleevelike portion 3" received in a fluidtight manner by the terminal portion of the bore 7 of the sleeve bolt 2.
  • valve seat 7 serves as a valve seat forming part of a disc valve.
  • the latter includes a valve plate 10 which is urged against said valve seat by a closing spring 11 supported at its end remote from the valve seat by a spring seat disc 12, which, in turn, is held by asetting screw 13 threadedly received in bore 7. It is seen that by turning the setting screw l3, the force of coil spring 11 may be varied.
  • the spring 11 engages the valve plate 10 offcenter which is achieved by providing the valve plate 10 with a guiding or support lug 14 secured eccentrically thereto and adapted to be surrounded by the spring 11. Further, the maximum diameter of the valve plate 10 is only slightly smaller than that of bore 7.
  • the axis of the coil spring 11 and that of the adjusting means 13 defines an angle which varies dependent upon the extent the spring 11 is compressed.
  • the setting screw 13 terminates in a cone 15, the apical portion of which nests in a conical depression 16 having a wider angle than that of cone 15.
  • Such a difference in the cone angles is necessary to prevent there the appearance of forces which would exert a bending moment on the spring 11.
  • the valve plate 10 has the shape of a truncated cone of small height; its base (i.e. its frontal face of larger diameter) is adjacent the insert 3.
  • its bore 6 is enlarged into a circular depression 17, the diameter of which is only very slightly smaller than the largest diameter of the valve plate 10.
  • a narrow fluidtight seat of this structure has the advantage that the specific sealing forces are relatively large, resulting in a good fluidtight seal. Also, the narrow valve seat face is automatically cleaned by the throughflowing fuel.
  • valve plate 10 almost the entire lower face of the valve plate 10 is affected by the fuel; consequently, the difference between the opening forces exerted on the closing element before and after the unseating of a valve plate 10 is small.
  • the valve plate surface acted upon by the opening pressure is that part of the valve plate base which lies inside the contour of the circular depression 17. After the unseating of valve plate 10, on the other hand, the only slightly larger entire base is exposed to the opening pressure.
  • the external face of the nozzle-body l is provided with a thread 19 by means of which the nozzle body may be screwed into a threaded tubular nozzle holder (not shown).
  • the nozzle holder then communicates with a pressure conduit, also not shown, leading from a delivery pump.
  • OPERATION OF THE EMBODIMENT flows across the bore 6 into the depression ll7 under the valve plate 10.
  • the valve plate 10 tilts about its edge overcoming the force of the spring 1 1, so that part of the heating oil may flow into the return channel 7.
  • the setting screw 13 into the setting screw 13 there are milled axial channels 23.
  • the axial position of the former in the latter may be changed thus varying the preload of spring 11, that is, varying the pressure required for the opening of the closing element.
  • This externally adjustable opening pressure determines the pressure prevailing in the turbulence chamber 4; the last-named pressure, in turn, determines the quantities to be injected through nozzle opening 5 into the firing zone.
  • a fuel injection nozzle of the known type that includes (A) a turbulence chamber, (B) supply conduit means merging into said turbulence chamber and delivering fuel under pressure thereto, (C) a nozzle opening in communication with said turbulence chamber, (D) a return channel in communication with said turbulence chamber, (E) a closing element disposed in said return channel and openable by the pressure prevailing in said turbulence chamber and (F) an adjustable closing spring disposed adjacent said closing element and urging the latter into a closed position against the force of said pressure, the improvement comprising, a disc valve constituting said closing element and having a valve plate provided with an edge, said closing spring engaging said valve plate offcenter to cause a tilting opening movement of said valve plate about a portion of said edge in response to the pressure prevailing in said turbulence chamber.
  • said turbulence chamber includes a cylindrical portion disposed remote from said noule opening, said fuel injection nozzle includes an axial bore constituting said return channel; said valve plate, said closing spring and said adjusting means are disposed in said bore.
  • valve plate is in the shape of a truncated cone tapering towards said closing spring, the largest diameter of said truncated cone is only slightly smaller than'the diameter of said bore.
  • valve seat cooperating with said valve plate, said valve seat has an opening which communicates with said turbulence chamber and has a diameter only slightly smaller than that face of the valve plate which cooperates with said valve seat.
  • said spring seat disc includes a conical depression in which the apical portion of said cone nests, the angle of said conical depression is larger than that of said cone.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US866244A 1968-11-02 1969-10-14 Fuel injection nozzle Expired - Lifetime US3587977A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681806674 DE1806674C3 (de) 1968-11-02 Einspritzdüse für flüssigen Brennstott insbesondere für Ölfeuerungen

Publications (1)

Publication Number Publication Date
US3587977A true US3587977A (en) 1971-06-28

Family

ID=5712212

Family Applications (1)

Application Number Title Priority Date Filing Date
US866244A Expired - Lifetime US3587977A (en) 1968-11-02 1969-10-14 Fuel injection nozzle

Country Status (3)

Country Link
US (1) US3587977A (fr)
DK (1) DK139244B (fr)
FR (1) FR2022484A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3693889A (en) * 1970-08-04 1972-09-26 Bosch Gmbh Robert Fuel injection nozzle
US4544097A (en) * 1982-11-29 1985-10-01 Diesel Kiki Company, Ltd. Fuel injection device
US5050799A (en) * 1985-08-15 1991-09-24 Ulrich Rohs Injection nozzle for liquid media
US20080164348A1 (en) * 2005-02-25 2008-07-10 Roman Brauneis Fuel Injector Comprising A Filter Unit
US20180306156A1 (en) * 2015-10-08 2018-10-25 Continental Automotive Gmbh Valve Assembly For An Injection Valve

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3693889A (en) * 1970-08-04 1972-09-26 Bosch Gmbh Robert Fuel injection nozzle
US4544097A (en) * 1982-11-29 1985-10-01 Diesel Kiki Company, Ltd. Fuel injection device
US5050799A (en) * 1985-08-15 1991-09-24 Ulrich Rohs Injection nozzle for liquid media
US20080164348A1 (en) * 2005-02-25 2008-07-10 Roman Brauneis Fuel Injector Comprising A Filter Unit
US7673817B2 (en) 2005-02-25 2010-03-09 Continental Automotive Gmbh Fuel injector comprising a filter unit
US20180306156A1 (en) * 2015-10-08 2018-10-25 Continental Automotive Gmbh Valve Assembly For An Injection Valve

Also Published As

Publication number Publication date
DK139244C (fr) 1979-06-18
DK139244B (da) 1979-01-15
DE1806674A1 (de) 1970-05-27
FR2022484A1 (fr) 1970-07-31
DE1806674B2 (de) 1976-02-12

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