EP0770176A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne

Info

Publication number
EP0770176A1
EP0770176A1 EP95937760A EP95937760A EP0770176A1 EP 0770176 A1 EP0770176 A1 EP 0770176A1 EP 95937760 A EP95937760 A EP 95937760A EP 95937760 A EP95937760 A EP 95937760A EP 0770176 A1 EP0770176 A1 EP 0770176A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
membrane
combustion chamber
injection
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.)
Ceased
Application number
EP95937760A
Other languages
German (de)
English (en)
Inventor
Karl Hofmann
Detlev Potz
Günter LEWENTZ
Uwe Gordon
Stefan Haug
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0770176A1 publication Critical patent/EP0770176A1/fr
Ceased legal-status Critical Current

Links

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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/047—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • the end face of a valve body on the combustion chamber side defines an annular pressure chamber into which an inlet line from the fuel injection pump opens.
  • the pressure chamber is delimited radially inwards by a pin projecting axially from the end face of the valve body, the cross section of which tapers conically at the end on the combustion chamber side to form a valve seat.
  • the pressure chamber is delimited by a disk-shaped valve membrane which is fastened to the valve body at its outer edge region with the interposition of a sleeve by means of a clamping nut and which has a central opening, the annular edge of which forms a sealing edge which interacts with the valve seat.
  • the valve membrane lies with its sealing surface in the closed state of the fuel injection valve under prestress against the valve seat, so that the pressure chamber is closed in the direction of the combustion chamber of the internal combustion engine to be supplied. If an injection is to take place, the pressure chamber acted upon by the supply line with high fuel pressure, which lifts the resilient valve membrane against the biasing force with its sealing surface from the valve seat.
  • the fuel injection takes place via the ring gap on the pin which is controlled in a manner analogous to known throttle pin nozzles.
  • the end of the injection process is controlled by stopping the high pressure supply in the pressure chamber.
  • the known fuel injection valve has the disadvantage that it is not suitable for use on direct-injection internal combustion engines, since only a single injection jet directed axially to the pin can be achieved with it.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage that the diaphragm nozzles, which are simple in terms of their construction, can now also be used for fuel injection devices for direct-injection internal combustion engines. This is advantageously made possible by the free choice of the arrangement of the injection openings downstream of the sealing seat, it now being possible to provide a large number of injection openings which are oriented in such a way that the injection jets are at a certain angle to the axis of the shaft of the injection valve, so that optimal fuel preparation is possible even in direct injection internal combustion engines.
  • valve seat can also be provided on a ball fastened to the end face of the valve body, which once again reduces the manufacturing outlay for the injection valve.
  • the injection openings downstream of the sealing surface can be introduced directly into a spherical shape of the preferably disc-shaped valve membrane or are provided in a separate insert which also carries the sealing surface and is then inserted into the valve membrane.
  • This two-piece construction of the valve membrane has the advantage that different materials can be used, so that a material with good spring properties can be used for the membrane and a material with good properties with regard to strength and durability can be used for the membrane insert.
  • Another advantage is achieved by the protrusion of the pin and the valve membrane into the combustion chamber, since the injection openings can be guided into a central area of the combustion chamber in this way.
  • valve diaphragm is advantageously fastened to the valve body by means of a clamping nut, an adjusting disk or ring being arranged between the valve diaphragm and the valve body in order to adjust the opening pressure of the injection valve. It is particularly advantageous to make the setting, for example, by means of a nut that is accessible from the outside, since in this way the opening pressure of the injection valve can still be made from the outside even after assembly.
  • valve membrane If a later adjustment is not necessary, it is alternatively possible to weld the valve membrane to a ring connected to the valve body.
  • a cap-shaped clamping nut By gripping the end face of the valve membrane on the combustion chamber side by means of a cap-shaped clamping nut, it is also advantageously possible to limit the opening stroke movement of the valve membrane, in order to ensure a defined flow cross section between the valve seat and the sealing surface.
  • Another advantage is achieved by fixing the rotational position of the movable valve member (valve membrane) towards the pin, so that no tension affecting the tightness can occur when there is frictional engagement between the clamping nut and the valve membrane.
  • FIG. 1 shows a longitudinal section through a first exemplary embodiment of the fuel injection valve according to the invention
  • FIG. 2 shows an enlarged view of the valve membrane and the valve seat formed by a pin
  • FIG. 3 shows a second exemplary embodiment in which the valve seat is formed by a ball
  • FIG. 4 is a third exemplary embodiment, in which an insert in the form of a truncated cone that receives the sealing surface and injection openings is inserted into the valve membrane
  • FIGS. 5 and 5A show a fourth exemplary embodiment in which the membrane insert is designed as a spherical segment, FIGS.
  • FIGS. 6 and 6A show a fifth exemplary embodiment in which the membrane insert is designed as a sphere, the spherical surface of which forms a valve sealing surface with which it connects with an outer surface 7 and 7A, a sixth embodiment with a valve seat formed on a ball and a conical membrane insert interacting with it, FIGS. 8 and 8A, a seventh embodiment with a ball valve seat and a ball or. spherical shape of the otherwise disk-shaped valve membrane, FIGS. 9 and 10 show an eighth and ninth exemplary embodiment in which the clamping nut engages around the valve membrane in a cap-shaped manner, FIG.
  • FIG. 11 shows a tenth exemplary embodiment in which the pin supporting the valve seat and the membrane extend axially the valve body protrude into the combustion chamber of the internal combustion engine and
  • FIG. 12 shows an eleventh embodiment in which the valve membrane and sleeve are formed in one piece.
  • a rotationally symmetrical valve body 1 shown in FIG. 1 has at one end a connection 3 for an inlet line, not shown, from a fuel injection pump, from which an inlet channel 5, which extends longitudinally through the valve body 1, leads away from one of the combustion chambers the end face 7 of the valve body 1 facing the internal combustion engine opens.
  • This end face 7 borders on a space 9 which, in the first exemplary embodiment shown enlarged in FIG. 2, is delimited radially inwards by a central pin 11 projecting axially from the end face 7 and radially outward by a sleeve 13 .
  • the frustoconical forms Pin 11 with a part of its conical surface has a valve seat 15 against which a valve membrane 17, which delimits the chamber 9 on the combustion chamber side and is preferably made of resilient steel and is curved in the direction of the chamber 9, comes under pressure with a sealing surface 19.
  • the disc-shaped valve membrane 17, which forms a movable valve member has a frusto-conical shape 21 (depression) at the level of the pin 11, the end of which is formed spherical, the end of the combustion chamber on the combustion chamber side, the inner flanks of the shape 21 having the valve seat 15 form cooperating valve sealing surface 19.
  • a blind-hole-shaped space 23 is formed, which is connected downstream of the sealing cross section formed between the valve seat 15 and the sealing surface 19 in the injection direction and downstream of which at least one, upstream preferably discharge a plurality of injection openings 25 into the combustion chamber of the internal combustion engine.
  • valve membrane 17 On its outer edge, the valve membrane 17 is tightly clamped against the valve body 1 by means of a clamping nut 27 with the sleeve 13 interposed, for which purpose the clamping nut 27 has a collar 29 covering the outer edge of the valve membrane 17.
  • the outside diameter of the valve membrane 17 is made smaller than the inside diameter of the clamping nut 27, so that the valve membrane 17 optimally fits to the pin during assembly 11 can center.
  • the fuel injection valve according to the invention is injected by filling the space 9 with fuel under high pressure from the injection pump via the inlet channel 5.
  • the valve membrane 17 with its sealing surface 19 becomes counter to it
  • Preload force is lifted from the valve seat 15, so that the fuel reaches the blind-hole-shaped space 23 along the now open sealing cross-section and further via the injection openings 25 into the combustion chamber of the internal combustion engine to be supplied.
  • the injection is terminated by interrupting the high-pressure fuel supply in the space 9, as a result of which the pressure in the space 9 drops again under the force of the prestressing of the valve membrane 17, so that the valve sealing surface 19 springs back onto the valve seat 15 in a sealing manner.
  • valve seat 15 is constructed analogously to the first exemplary embodiment shown in FIGS. 1 and 2.
  • the valve seat 15 is formed there by a preferably welded ball 31 fastened in the middle of the end face 7 of the valve body 1, the surface of which forms the valve seat 15, which cooperates with the valve sealing face 19 of the valve membrane 17.
  • FIG. 4 shows a third exemplary embodiment in which the valve membrane 17 is constructed in two parts. Sealing surface 19 and injection openings 25 are arranged on a membrane insert 33, the shape of which corresponds to the shape 21 of FIG. 2 and which is inserted into a provided receiving bore 35 of valve membrane 17 and fastened in a sealing manner.
  • FIG. 5 and in an enlarged section 5A show a fourth embodiment of the fuel injection valve, in which the membrane insert 33 is formed as a hollow ball 37, on the side facing the space 9 an opening is provided, the walls of which are the valve sealing surface Form 19 and into which the pin 11 projects with its valve seat 15.
  • the valve seat 15 is formed by the opening of the inlet channel 5 in the end face 7 of the valve body 1.
  • the valve sealing surface 19 cooperating with this valve seat 15 is formed on a solid ball 39 which is connected to the valve membrane 17 and which is penetrated by intersecting bores 41 which form the injection openings 25 and which, starting from the space 9, enter the combustion chamber of the internal combustion engine flow out.
  • the space 9 which is permanently connected to the combustion chamber, takes over the function of the pocket-shaped space 23 during the operation of the fuel injection valve, the previous figures and the pressure in the inlet channel 5 flows directly against the valve sealing surface 19 of the valve membrane 17
  • the sleeve 13 is also inserted into this dead volume between the valve membrane 17 and the valve body 1, which is designed such that it controls the opening and closing movement of the valve membrane 17 not affected.
  • the sixth exemplary embodiment shown in FIGS. 7 and 7A is a combination of the valve seat 15 formed on the ball 31 and a valve sealing surface 19 according to FIGS. 3 and 7 arranged on the membrane insert 33.
  • the seventh exemplary embodiment shown in FIG. 8 and enlarged in FIG. 8A differs from the second exemplary embodiment shown in FIG. 3 only in the shape of the shape 21 on the valve membrane 17, which is now designed in the shape of a spherical cap, the intermediate spherical bottom and Valve seat ball 31 formed blind hole-shaped space 23, from which the injection openings 25 lead, is limited to reduce the volume of damage.
  • valve membrane 17 is approximately bell-shaped with an Sets formed
  • the clamping nut 27 presses the valve membrane 17 via an annular shoulder 43 directly against the end face 7 of the valve body 1.
  • the collar 29 of the clamping nut 27 projects radially inwards so far that it reaches the valve membrane 17 except for a small, adjustable gap dimension s, the size of the gap dimension s thus determining the maximum opening stroke of the valve membrane 17
  • the ninth exemplary embodiment shown differs from the eighth exemplary embodiment only in that an adjusting ring 45 is clamped between the end face 7 of the valve body 1 and the valve diaphragm 17, the strength or deformation of which adjusts the axial position of the valve diaphragm 17 to the valve body 1 and thus can set the biasing force of the system of valve sealing surface 19 on the valve seat 15 or the opening pressure of the fuel injector.
  • valve membrane 17 protrude from the overlap with the clamping nut 27 into the interior of the combustion chamber of the internal combustion engine, the valve membrane 17 during the pressurization of the space 9 in addition to an expansion the opening cross-section between valve seat 15 and valve sealing surface 19 also opens in the axial direction to valve body 1 by means of radial breathing.
  • valve membrane 17, which is otherwise designed analogously to FIG. 1, is made in one piece with the sleeve 13 from FIG.
  • there is no sealing joint which leads to less machining effort and, at the same time, a reduction in the risk of leaks.
  • a further advantage is the transition area that continuously merges into the sleeve, through which the stresses at the clamping point of the valve membrane can be reduced. It is thus possible with the fuel injection valve according to the invention to combine the advantages of a perforated nozzle with the advantages of a diaphragm nozzle in a structurally simple manner and thus to ensure high functional reliability when using fewer components.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape d'injection de carburant pour moteurs à combustion interne, qui comprend un corps (1), à l'extrémité située côté chambre de combustion duquel se trouve une chambre (9) reliée à un canal d'arrivée (5) et délimitée en dedans dans le sens radial par un tourillon (11) faisant saillie dans le sens axial, depuis la surface d'about (7) du corps de la soupape, située côté chambre de combustion, et portant un siège de soupape (15). Cette soupape d'injection de carburant comprend également une membrane (17) faisant ressort, qui délimite l'espace (9) allant jusqu'à la chambre de combustion du moteur à combustion interne à alimenter, et est fixée tendue au niveau de sa zone marginale extérieure, sur le corps de la soupape (1). Sur cette membrane (17), il est prévu une surface d'étanchéité (19) de la soupape, appliquée tendue de manière étanche sur le siège (15) de soupape. La membrane (17) de la soupape comporte des orifices d'injection (25) situés dans le sens d'écoulement du carburant injecté, derrière la surface d'étanchéité (19), sur ladite membrane (17).
EP95937760A 1994-12-20 1995-11-15 Soupape d'injection de carburant pour moteurs a combustion interne Ceased EP0770176A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4445585 1994-12-20
DE4445585A DE4445585A1 (de) 1994-12-20 1994-12-20 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/DE1995/001580 WO1996019660A1 (fr) 1994-12-20 1995-11-15 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (1)

Publication Number Publication Date
EP0770176A1 true EP0770176A1 (fr) 1997-05-02

Family

ID=6536448

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95937760A Ceased EP0770176A1 (fr) 1994-12-20 1995-11-15 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (7)

Country Link
EP (1) EP0770176A1 (fr)
JP (1) JPH09509717A (fr)
KR (1) KR970701310A (fr)
CN (1) CN1141664A (fr)
CZ (1) CZ241596A3 (fr)
DE (1) DE4445585A1 (fr)
WO (1) WO1996019660A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19536330A1 (de) * 1995-09-29 1997-04-03 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10064802A1 (de) * 2000-12-22 2002-06-27 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1559905A1 (fr) * 2004-01-29 2005-08-03 Siemens VDO Automotive S.p.A. Injecteur de fluide avec une aiguille de soupape deformable
DE102008007203A1 (de) * 2008-02-01 2009-08-06 Robert Bosch Gmbh Kompakte Einspritzvorrichtung mit druckgesteuerter Düse
TWI470149B (zh) * 2009-02-12 2015-01-21 Bosch Gmbh Robert 具有受壓力控制的噴嘴的緊密式噴油裝置
CN101592106B (zh) * 2009-04-24 2013-10-30 靳北彪 发动机用有孔阀片形变燃油喷射器
CN101592112B (zh) * 2009-04-24 2012-06-27 靳北彪 发动机用阀片形变燃油喷射器
CN101598096B (zh) * 2009-05-12 2012-04-25 靳北彪 发动机用全域燃油喷射装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE363572C (de) * 1922-11-10 Oskar Robert Groenkwist Vorrichtung zum Zerstaeuben von Fluessigkeiten, insbesondere von fluessigem Brennstoff fuer Verbrennungskraftmaschinen
DE497439C (de) * 1926-03-28 1930-05-09 Super Diesel Tractor Corp Verfahren und Vorrichtung zur luftlosen Einfuehrung fluessigen Brennstoffs in gasfoermigem Zustand in den Arbeitsraum einer Brennkraftmaschine
US2805891A (en) * 1954-04-05 1957-09-10 Mcculloch Motors Corp Fluid spray nozzle
GB760852A (en) * 1954-06-11 1956-11-07 Dewandre Co Ltd C Improvements relating to fuel injection nozzles for internal combustion engines including gas turbines
FR1218966A (fr) * 1958-03-25 1960-05-13 Motorpal Jihlava Np Buse d'injection pour injecteur de moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9619660A1 *

Also Published As

Publication number Publication date
DE4445585A1 (de) 1996-06-27
CN1141664A (zh) 1997-01-29
CZ241596A3 (en) 1997-02-12
JPH09509717A (ja) 1997-09-30
WO1996019660A1 (fr) 1996-06-27
KR970701310A (ko) 1997-03-17

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