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WO2001075298A1 - Fuel injection valve for an internal combustion engine - Google Patents

Fuel injection valve for an internal combustion engine Download PDF

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Publication number
WO2001075298A1
WO2001075298A1 PCT/DE2001/001271 DE0101271W WO0175298A1 WO 2001075298 A1 WO2001075298 A1 WO 2001075298A1 DE 0101271 W DE0101271 W DE 0101271W WO 0175298 A1 WO0175298 A1 WO 0175298A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
bore
valve body
section
combustion 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.)
Ceased
Application number
PCT/DE2001/001271
Other languages
German (de)
French (fr)
Inventor
Werner Wagner
Wilhelm Eyberg
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 WO2001075298A1 publication Critical patent/WO2001075298A1/en
Anticipated expiration legal-status Critical
Ceased 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

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 example from the patent DE 42 05 744 C2.
  • a bore is formed in a valve body, in which a piston-shaped valve member is arranged to be longitudinally displaceable. At least one injection opening is formed at the end of the bore on the combustion chamber side
  • Valve member is opened and closed.
  • the valve member is sealingly guided in the bore in a section facing away from the combustion chamber, tapers towards the combustion chamber with the formation of a pressure shoulder and merges into a stem part.
  • the pressure shoulder is arranged in a pressure chamber which surrounds the valve member and is formed by a radial expansion of the bore.
  • the pressure chamber continues to the combustion chamber as an annular channel surrounding the valve member and is connected to a high-pressure fuel source via an inlet channel running in the valve body.
  • the design of the pressure chamber as a radial extension of the bore is difficult to manufacture in the known fuel injection valve. Since the pressure chamber only over the section of the bore, the sealing section the valve member receives, accessible st, the manufacture of the pressure chamber is complex and expensive. Due to the high fuel pressure with which the fuel flows out of the inlet channel into the pressure chamber, all edges and transitions of the pressure chamber have to be rounded in order to avoid turbulence and sharp notches. Because of the difficult access to the location of the pressure chamber, this is also complex and therefore cost-intensive.
  • valve body consists of two valve body parts, the separating surface of the valve body parts dividing the pressure chamber.
  • each valve body part can be manufactured separately and, since it is now easily accessible, the pressure chamber can be designed simply and inexpensively.
  • the first valve body part is advantageously axially braced against the second valve body part, care being taken to ensure that the bores in the first and second valve body parts are exactly aligned. It is advantageous here to guide the stem part of the valve member near the injection openings in addition to the sealingly guided section of the valve member.
  • valve sealing surface formed on the valve member cooperates optimally with the valve seat, even if the bore in the first and the bore in the second valve body part are not exactly aligned with one another, which will generally be the case due to the manufacturing tolerances. Due to the comparatively long
  • valve member between the additional guidance of the valve stem and the sealingly guided section of the valve member the valve member is flexible enough to allow a slight deviation from the exact alignment of the two guides to compensate without seizing the valve member in the bore.
  • the fuel injection valve according to the invention has the advantage that the bore in the first and second valve body parts can have a different diameter.
  • the diameter of the bore in the valve body part facing the combustion chamber can be made larger than the diameter of the bore in the valve body part facing away from the combustion chamber.
  • FIG. 1 shows a longitudinal section through the fuel injection valve according to the invention.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention, as is used for injecting fuel into the combustion chamber of an internal combustion engine.
  • a valve body 1 is clamped axially against a valve holding body 5 with a clamping nut 2.
  • the valve body 1 is composed of two valve body parts 101 and 201, the first valve body part 101 facing away from the combustion chamber and the second valve body part 201 facing the combustion chamber, so that the first valve body part 101 is arranged between the valve holding body 5 and the second valve body part 201.
  • the first valve body part 101 has a cylindrical outer contour and rests with its end face facing the combustion chamber against the end face of the second valve body part 201.
  • the outer surface of the second valve body part 201 is stepped Cylinder formed, the outer diameter of the second valve body part 201 is reduced to form the annular shoulder 19 to the combustion chamber hm.
  • a centering bore 32 is formed in the mutually facing end faces of the valve holding body 5 and the first valve body part 101, which run parallel to the longitudinal axis 35 of the valve body 1 and are aligned with the intended mounting position of the valve body parts 101, 201.
  • identical center holes 32 are formed on the mutually facing end faces of the first valve body part 101 and the second valve body part 201.
  • Centering pins 30 are arranged in the centering bores 32 and ensure that the valve holding body 5 and the valve body parts 101 and 201 maintain the intended position with respect to one another. It can also be provided that more than one centering bore 32 is formed on the end faces of the valve body parts 101, 201 or the valve holding body.
  • a bore 6 is formed in the valve body 1, one end of which is closed and faces the combustion chamber.
  • the bore 6 extends through the first valve body part 101 to close to the combustion chamber end of the second valve body part 201, so that a first section 106 of the
  • Bore 6 is formed in the first valve body part 101 and a second section 206 of the bore 6 in the second valve body part 201.
  • a valve seat 22 and at least one injection opening 24 are formed which connect the bore 6 with the combustion chamber of the internal combustion engine combines.
  • a piston-shaped valve member 9 is arranged so as to be longitudinally displaceable, which is sealingly guided by a sealing section 109 in the first section 106 of the bore 6.
  • the valve member 9 tapers to the combustion chamber with formation a pressure shoulder 13 and merges into a shaft part 209.
  • a valve sealing surface 20 is formed, with which the valve member 9 cooperates with the valve seat 22 for controlling the at least one injection opening 24.
  • the pressure shoulder 13 is arranged in a pressure space 28 which surrounds the valve member 9 and is formed by a radial expansion of the bore 6 and which continues as an annular channel surrounding the stem part 209 of the valve member 9 up to the valve seat 22.
  • the pressure chamber 28 is connected via an inlet channel 26 running in the valve body 1 and the valve holding body 5 to a high-pressure fuel source, not shown in the drawing, and can be filled with fuel under high pressure.
  • the valve member 9 has a radial extension 10 on the shaft part 209, with which the valve member 9 is guided in the first section 106 of the bore 6.
  • 10 recesses 11 are formed on the radial extension.
  • longitudinal grooves or oblique grooves extending obliquely to the longitudinal axis 35 of the valve body 1 are formed on the radial extension 10.
  • the valve member 9 merges away from the combustion chamber into a spring plate 17 which is arranged in a spring chamber 16 formed in the valve holding body 5.
  • the spring 15 is arranged between the spring plate 17 and a spring stop (not shown in the drawing) under prestress and acts on the valve member 9 in the direction of the valve seat 22.
  • the mode of operation of the fuel injection valve is as follows: via the high-pressure fuel source, not shown in the drawing, fuel is introduced into the inlet channel 26, so that a predetermined high level of fuel pressure prevails in the pressure chamber 28 down to the valve seat 22.
  • the pressure of the fuel in the pressure chamber 28 results in a force acting in the axial direction of the valve member 9 on the pressure shoulder 13, which acts on the valve member 9 away from the combustion chamber.
  • a closing force is exerted on the valve member 9 by the valve piston 12, which is greater than the hydraulic force on the pressure shoulder 13, so that the valve member 9 rests with the valve sealing surface 20 on the valve seat 22 and the at least one injection opening 24 against the hole 6 seals.
  • the injection process is initiated in that the hydraulically generated closing force on the valve piston 12 is reduced to such an extent that it is less than the hydraulic force on the pressure shoulder 13 of the valve member 9.
  • the valve member 9 experiences a resulting force which is directed away from the combustion chamber is so that the valve member 9 with the valve sealing surface 20 lifts off the valve seat 22 and opens at least one injection opening 24.
  • the fuel from the pressure chamber 28 is now injected into the combustion chamber of the internal combustion engine via the at least one injection opening 24.
  • the injection is ended by increasing the hydraulically generated closing force on the valve piston 12 to such an extent that the force thereby generated on the valve member 9 is greater than the hydraulic force on the Pressure shoulder 13 and the valve sealing surface 20.
  • the valve member 9 is thereby pressed again with the valve sealing surface 20 against the valve seat 22 and thus closes the at least one injection opening 24.
  • the spring 15 mainly serves to keep the fuel injection valve closed when the internal combustion engine is switched off and thus in the depressurized state in the pressure chamber 28.
  • both valve body parts 101 and 201 can be manufactured separately from one another. It should be ensured here that the sections 106 and 206 of the bore 6 in the installed position of the valve body parts 101 and 201 are exactly aligned with one another.
  • the parting plane of the two valve body parts 101 and 201 divides the pressure chamber 28. This makes it easily possible to carefully round the transitions from the pressure chamber 28 to the bore 6 and the transition from the inlet channel 26 to the pressure chamber 28. On the one hand, this is necessary in order to prevent swirling of the fuel in the area of the pressure chamber 28, which would result in the fuel injector not functioning optimally. On the other hand, rounding avoids sharp
  • valve member 9 near the valve seat 22 through the radial extension 10 in the second section 206 of the bore 6 leads, there is an exactly symmetrical position of the valve seal - flat 20 with respect to the valve seat 22.
  • all the injection openings 24 are opened uniformly during the opening stroke movement of the valve member 9 and the injection of the fuel m into the combustion chamber of the internal combustion engine takes place correspondingly uniformly through all injection openings 24. This ensures optimal combustion and the lowest possible exhaust gas values.
  • valve body 1 is connected to a valve holding body 5, in which the closing force is not exerted hydraulically on the valve member 9 via a valve piston 12, but is generated by one or more springs.
  • the control of the injection process does not take place via a change in the closing force on the valve member 9, but with an at least approximately constant closing force via a pressure change in the pressure chamber 28.
  • the valve member 9 opens the at least one injection opening in the manner described above 24, when the fuel pressure drops, it is pressed against the valve seat 22 again by the closing force and the injection openings 24 are closed.
  • valve member 9 Due to the additional second guidance of the valve member 9 m of the bore 6 and the large distance between the sealingly guided section of the valve member 9 to this additional guide, the valve member 9 is flexible enough to compensate for a slight roofing of the two sections 106 and 206 of the bore 6, without causing the valve member 9 to seize in the bore 6.
  • valve member 9 As an alternative to the additional guidance of the valve member 9 shown in the drawing, provision can also be made for the guidance not to be formed by a radial widening 10 of the valve member 9, but by a radial narrowing of the bore 6.
  • the guidance not to be formed by a radial widening 10 of the valve member 9, but by a radial narrowing of the bore 6.
  • precautions must be taken that: allow an inflow of fuel from the pressure chamber 28 to the injection openings 24, for example recesses on the radial constriction or on the valve member 9 in the region of the radial constriction.

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

Abstract

The invention relates to a fuel injection valve, comprising a valve body (1), provided with a bore (6) which is closed on the combustion chamber end and forms a valve seat (9) there. A piston-shaped valve member (9) which is tapered towards the combustion chamber while forming a pressure shoulder (13) is disposed in the bore (6) and interacts with the valve seat (22) with a valve stem (20) configured at the combustion chamber end. The pressure shoulder (13) is disposed in a pressure chamber (28) formed in the valve body (1), which may be filled with fuel under high pressure. The valve member (9) is guided in a combustion chamber distal first section (106) in the bore (6) and is provided with a second guide configured by a radial enlargement (10) in the direction of the valve seat (22), said second guide being disposed in a second section of the bore (206). The valve body (1) consists of two parts, the first section (106) of the bore (6) being disposed in the first valve body portion (101), and the second section (206) of the bore (6) being disposed in the second valve body portion (201), so that the two valve body portions (101, 201) can be produced individually and the pressure chamber (28) can be designed as a more lightweight part, thereby reducing production costs.

Description

Kraftstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Ein solches Kraftstoffeinspritzventil ist beispielsweise aus der Patentschrift DE 42 05 744 C2 bekannt. In einem Ventilkörper ist eine Bohrung ausgebildet, in der ein kolbenförmiges Ventilglied längsverschiebbar angeordnet ist. Am brennraumseitigen Ende der Bohrung ist wenigstens eine Ein- spritzöffnung ausgebildet, die durch die Längsbewegung desThe invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is known for example from the patent DE 42 05 744 C2. A bore is formed in a valve body, in which a piston-shaped valve member is arranged to be longitudinally displaceable. At least one injection opening is formed at the end of the bore on the combustion chamber side

Ventilgliedes auf- und zugesteuert wird. Das Ventilglied ist in einem brennraumabgewandten Abschnitt dichtend in der Bohrung geführt, verjüngt sich zum Brennraum hin unter Bildung einer Druckschulter und geht in einen Schaftteil über. Die Druckschulter ist in einem Druckraum angeordnet, der das Ventilglied umgibt und durch eine radiale Erweiterung der Bohrung gebildet ist. Der Druckraum setzt sich dem Brennraum zu als ein das Ventilglied umgebender Ringkanal fort und ist über einen im Ventilkörper verlaufenden Zulaufkanal mit ei- ner Kraftstoffhochdruckquelle verbunden.Valve member is opened and closed. The valve member is sealingly guided in the bore in a section facing away from the combustion chamber, tapers towards the combustion chamber with the formation of a pressure shoulder and merges into a stem part. The pressure shoulder is arranged in a pressure chamber which surrounds the valve member and is formed by a radial expansion of the bore. The pressure chamber continues to the combustion chamber as an annular channel surrounding the valve member and is connected to a high-pressure fuel source via an inlet channel running in the valve body.

Die Ausbildung des Druckraumes als radiale Erweiterung der Bohrung ist bei dem bekannten Kraftstoffeinspritzventil schwierig zu fertigen. Da der Druckraum nur über den Ab- schnitt der Bohrung, der den dichtend geführten Abschnitt des Ventilgliedes aufnimmt, zugänglich st, ist die Fertigung des Druckraums aufwendig und teuer. Aufgrund des hohen Kraf stoffdrucks , mit dem der Kraftstoff aus dem Zulaufkanal m den Druckraum strömt, müssen alle Kanten und Übergänge des Druckraums aufwendig gerundet werden, damit Verwirbelun- gen und scharfe Kerben vermieden werden. Auch dies ist aufgrund der schwer zugänglichen Lage des Druckraums aufwendig und damit kostenintensiv.The design of the pressure chamber as a radial extension of the bore is difficult to manufacture in the known fuel injection valve. Since the pressure chamber only over the section of the bore, the sealing section the valve member receives, accessible st, the manufacture of the pressure chamber is complex and expensive. Due to the high fuel pressure with which the fuel flows out of the inlet channel into the pressure chamber, all edges and transitions of the pressure chamber have to be rounded in order to avoid turbulence and sharp notches. Because of the difficult access to the location of the pressure chamber, this is also complex and therefore cost-intensive.

Vorteile der ErfindungAdvantages of the invention

Das erfmdungsgemaße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der Ventilkörper aus zwei Ventilkörpertei- len besteht, wobei die Trennfläche der Ventilkörperteile den Druckraum teilt. Dadurch kann jedes Ventilkörperteil separat gefertigt werden und der Druckraum kann, da er nun gut zugänglich ist, einfach und kostengünstig ausgebildet werden. Das erste Ventilkörperteil ist gegen das zweite Ventilkör- perteil m vorteilhaf er Weise axial verspannt, wobei darauf geachtet werden muß, daß die Bohrungen im ersten und zweiten Ventilkörperteil genau fluchten. Hierbei ist es vorteilhaft, den Schaftteil des Ventilgliedes nahe den Einspritzöffnungen zusätzlich zum dichtend geführten Abschnitt des Ventilglie- des zu führen. Nur dadurch arbeitet die am Ventilglied ausgebildete Ventildichtflache optimal mit dem Ventilsitz zusammen, auch dann, wenn die Bohrung im ersten und die Bohrung im zweiten Ventilkörperteil nicht ganz exakt zueinander fluchten, was bedingt durch die Fertigungstoleranzen m der Regel der Fall sein wird. Durch den vergleichsweise langenThe fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the valve body consists of two valve body parts, the separating surface of the valve body parts dividing the pressure chamber. As a result, each valve body part can be manufactured separately and, since it is now easily accessible, the pressure chamber can be designed simply and inexpensively. The first valve body part is advantageously axially braced against the second valve body part, care being taken to ensure that the bores in the first and second valve body parts are exactly aligned. It is advantageous here to guide the stem part of the valve member near the injection openings in addition to the sealingly guided section of the valve member. This is the only way that the valve sealing surface formed on the valve member cooperates optimally with the valve seat, even if the bore in the first and the bore in the second valve body part are not exactly aligned with one another, which will generally be the case due to the manufacturing tolerances. Due to the comparatively long

Ventilgliedschaft zwischen der zusätzlichen Führung des Ven- tilschaftes und dem dichtend geführten Abschnitt des Ventilgliedes ist das Ventilglied flexibel genug, um eine leichte Abweichung aus der genauen Fluchtung der beiden Führungen auszugleichen, ohne daß es zu einem Fressen des Ventilgliedes in der Bohrung kommt .Valve member between the additional guidance of the valve stem and the sealingly guided section of the valve member, the valve member is flexible enough to allow a slight deviation from the exact alignment of the two guides to compensate without seizing the valve member in the bore.

Darüber hinaus bietet das erfindungsgemäße Kraftstoffein- spritzventil den Vorteil, daß die Bohrung im ersten und zweiten Ventilkörperteil einen unterschiedlichen Durchmesser aufweisen kann. Insbesondere kann der Durchmesser der Bohrung in dem dem Brennraum zugewandten Ventilkörperteil größer ausgebildet sein als der Durchmesser der Bohrung in dem dem Brennraum abgewandten Ventilkörperteil.In addition, the fuel injection valve according to the invention has the advantage that the bore in the first and second valve body parts can have a different diameter. In particular, the diameter of the bore in the valve body part facing the combustion chamber can be made larger than the diameter of the bore in the valve body part facing away from the combustion chamber.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungs- gemäßen Kraftstoffeinspritzventils gezeigt. In der Figur 1 ist ein Längsschnitt durch das erfindungsgemäße Kraftstoffeinspritzventil dargestellt.An exemplary embodiment of the fuel injection valve according to the invention is shown in the drawing. 1 shows a longitudinal section through the fuel injection valve according to the invention.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In der Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil gezeigt, wie es zur Einspritzung von Kraftstoff in den Brennraum einer Brennkraftmaschine verwendet wird. Ein Ventilkörper 1 ist mit einer Spannmutter 2 axial gegen einen Ventilhaltekörper 5 verspannt. Der Ventilkörper 1 ist aus zwei Ventilkörperteilen 101 und 201 zusammengesetzt, wobei das erste Ventilkörperteil 101 brennraumabgewandt und das zweite Ventilkörperteil 201 brennraumzugewandt angeordnet ist, so daß das erste Ven- tilkörperteil 101 zwischen dem Ventilhaltekörper 5 und dem zweiten Ventilkörperteil 201 angeordnet ist. Das erste Ventilkörperteil 101 weist eine zylindrische Außenkontur auf und liegt mit seiner brennraumzugewandten Stirnfläche an der Stirnfläche des zweiten Ventilkörperteils 201 an. Die Außen- fläche des zweiten Ventilkörperteils 201 ist als gestufter Zylinder ausgebildet, wobei sich der Außendurchmesser des zweiten Ventilkörperteils 201 unter Bildung einer Ringschulter 19 zum Brennraum hm verringert.FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention, as is used for injecting fuel into the combustion chamber of an internal combustion engine. A valve body 1 is clamped axially against a valve holding body 5 with a clamping nut 2. The valve body 1 is composed of two valve body parts 101 and 201, the first valve body part 101 facing away from the combustion chamber and the second valve body part 201 facing the combustion chamber, so that the first valve body part 101 is arranged between the valve holding body 5 and the second valve body part 201. The first valve body part 101 has a cylindrical outer contour and rests with its end face facing the combustion chamber against the end face of the second valve body part 201. The outer surface of the second valve body part 201 is stepped Cylinder formed, the outer diameter of the second valve body part 201 is reduced to form the annular shoulder 19 to the combustion chamber hm.

In den aneinander zugewandten Stirnflächen von Ventilhalte- körper 5 und erstem Ventilkörperteil 101 ist jeweils eine Zentrierbohrung 32 ausgebildet, die parallel zur Längsachse 35 des Ventilkorpers 1 verlaufen und m der vorgesehenen Montageposition der Ventilkörperteile 101,201 fluchtend an- geordnet sind. Entsprechend sind gleich ausgebildete Zentrierbohrungen 32 an den einander zugewandten Stirnflächen von erstem Ventilkörperteil 101 und zweitem Ventilkörperteil 201 ausgebildet. In den Zentrierbohrungen 32 sind Zentrierstifte 30 angeordnet, die dafür sorgen, daß der Ventilhalte- körper 5 und die Ventilkörperteile 101 und 201 die vorgesehene Position zueinander einhalten. Es kann auch vorgesehen sein, mehr als eine Zentrierbohrung 32 an den Stirnflächen der Ventilkörperteile 101,201 bzw. des Ventilhaltekörpers auszubilden.A centering bore 32 is formed in the mutually facing end faces of the valve holding body 5 and the first valve body part 101, which run parallel to the longitudinal axis 35 of the valve body 1 and are aligned with the intended mounting position of the valve body parts 101, 201. Correspondingly, identical center holes 32 are formed on the mutually facing end faces of the first valve body part 101 and the second valve body part 201. Centering pins 30 are arranged in the centering bores 32 and ensure that the valve holding body 5 and the valve body parts 101 and 201 maintain the intended position with respect to one another. It can also be provided that more than one centering bore 32 is formed on the end faces of the valve body parts 101, 201 or the valve holding body.

Im Ventilkörper 1 ist eine Bohrung 6 ausgebildet, deren eines Ende geschlossen ist und dem Brennraum zugewandt ist. Die Bohrung 6 erstreckt sich durch den ersten Ventilkörperteil 101 bis nahe an das brennraumseitige Ende des zweiten Ventilkörperteils 201, so daß ein erster Abschnitt 106 derA bore 6 is formed in the valve body 1, one end of which is closed and faces the combustion chamber. The bore 6 extends through the first valve body part 101 to close to the combustion chamber end of the second valve body part 201, so that a first section 106 of the

Bohrung 6 ist im ersten Ventilkörperteil 101 ausgebildet ist und ein zweiter Abschnitt 206 der Bohrung 6 im zweiten Ventilkörperteil 201. Am dem Brennraum zugewandten Ende des Bohrungsabschnitts 206 ist ein Ventilsitz 22 und wenigstens eine Einspritzöffnung 24 ausgebildet, die die Bohrung 6 mit dem Brennraum der Brennkraftmaschine verbindet. In der Bohrung 6 ist e n kolbenförmiges Ventilglied 9 längsverschieb- bar angeordnet, welches mit einem Dichtungsabschnitt 109 im ersten Abschnitt 106 der Bohrung 6 dichtend gefuhrt ist. Dem Brennraum zu verjüngt sich das Ventilglied 9 unter Bildung einer Druckschulter 13 und geht in einen Schaftteil 209 über. Am brennraumseitigen Ende des Ventilgliedes 9 ist eine Ventildichtfläche 20 ausgebildet, mit der das Ventilglied 9 mit dem Ventilsitz 22 zur Steuerung der wenigstens einen Einspritzöffnung 24 zusammenwirkt. Die Druckschulter 13 ist in einem das Ventilglied 9 umgebenden und durch eine radiale Erweiterung der Bohrung 6 gebildeten Druckraum 28 angeordnet, der sich als ein den Schaftteil 209 des Ventilgliedes 9 umgebender Ringkanal bis zum Ventilsitz 22 fortsetzt. Der Druckraum 28 ist über einen im Ventilkörper 1 und dem Ventilhaltekörper 5 verlaufenden Zulaufkanal 26 mit einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle verbunden und kann darüber mit Kraftstoff unter hohem Druck befüllt werden.Bore 6 is formed in the first valve body part 101 and a second section 206 of the bore 6 in the second valve body part 201. At the end of the bore section 206 facing the combustion chamber, a valve seat 22 and at least one injection opening 24 are formed which connect the bore 6 with the combustion chamber of the internal combustion engine combines. In the bore 6, a piston-shaped valve member 9 is arranged so as to be longitudinally displaceable, which is sealingly guided by a sealing section 109 in the first section 106 of the bore 6. The valve member 9 tapers to the combustion chamber with formation a pressure shoulder 13 and merges into a shaft part 209. At the end of the valve member 9 on the combustion chamber side, a valve sealing surface 20 is formed, with which the valve member 9 cooperates with the valve seat 22 for controlling the at least one injection opening 24. The pressure shoulder 13 is arranged in a pressure space 28 which surrounds the valve member 9 and is formed by a radial expansion of the bore 6 and which continues as an annular channel surrounding the stem part 209 of the valve member 9 up to the valve seat 22. The pressure chamber 28 is connected via an inlet channel 26 running in the valve body 1 and the valve holding body 5 to a high-pressure fuel source, not shown in the drawing, and can be filled with fuel under high pressure.

Das Ventilglied 9 weist am Schaftteil 209 eine radiale Erweiterung 10 auf, mit der das Ventilglied 9 im ersten Abschnitt 106 der Bohrung 6 geführt ist. Um dem Kraftstoff den Durchfluß vom Druckraum 28 zum Ventilsitz 22 und weiter zu den Einspritzöffnungen 24 zu ermöglichen, sind an der radialen Erweiterung 10 Ausnehmungen 11 ausgebildet. Statt der Ausnehmungen 11 kann es auch vorgesehen sein, daß an der radialen Erweiterung 10 Längsnuten oder schräg zur Längsachse 35 des Ventilkörpers 1 verlaufende Schrägnuten ausgebildet sind. Darüber hinaus ist es auch möglich, den Kraftstofffluß durch Bohrungen sicherzustellen, die von einer Stirnseite zur gegenüberliegenden Stirnseite der radialen Erweiterung 10 führen.The valve member 9 has a radial extension 10 on the shaft part 209, with which the valve member 9 is guided in the first section 106 of the bore 6. In order to allow the fuel to flow from the pressure chamber 28 to the valve seat 22 and further to the injection openings 24, 10 recesses 11 are formed on the radial extension. Instead of the recesses 11, it can also be provided that longitudinal grooves or oblique grooves extending obliquely to the longitudinal axis 35 of the valve body 1 are formed on the radial extension 10. In addition, it is also possible to ensure the fuel flow through bores which lead from one end face to the opposite end face of the radial extension 10.

Das Ventilglied 9 geht brennraumabgewandt in einen Federteller 17 über, der in einem im Ventilhaltekörper 5 ausgebildeten Federraum 16 angeordnet ist. Die Feder 15 ist zwischen dem Federteller 17 und einem in der Zeichnung nicht dargestellten Federanschlag unter Vorspannung angeordnet und be- aufschlagt das Ventilglied 9 in Richtung auf den Ventilsitz 22. Am Federteller 17 kommt darüber hinaus ein Ventilkolben 12 zur Anlage, der koaxial zur Längsachse 35 des Ventilgliedes 9 angeordnet ist und der hydraulisch gesteuert eine Kraft in Richtung auf den Ventilsitz 22 auf das Ventilglied 9 ausüben kann.The valve member 9 merges away from the combustion chamber into a spring plate 17 which is arranged in a spring chamber 16 formed in the valve holding body 5. The spring 15 is arranged between the spring plate 17 and a spring stop (not shown in the drawing) under prestress and acts on the valve member 9 in the direction of the valve seat 22. On the spring plate 17 there is also a valve piston 12 which is arranged coaxially to the longitudinal axis 35 of the valve member 9 and which can be hydraulically controlled to exert a force in the direction of the valve seat 22 on the valve member 9.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Über die in der Zeichnung nicht dargestellte Kraftstoffhochdruckquelle wird Kraftstoff in den Zulaufkanal 26 eingeführt, so daß im Druckraum 28 bis hinunter zum Ventilsitz 22 ein vorgegebenes hohes Kraf stoffdruckniveau herrscht. Durch den Druck des Kraftstoffs im Druckraum 28 ergibt sich eine in axialer Richtung des Ventilgliedes 9 wirkende Kraft auf die Druckschulter 13, die das Ventilglied 9 vom Brennraum weg beaufschlagt. Im geschlossenen Zustand des Kraftstoffeinspritzventils wird durch den Ventilkolben 12 eine Schließkraft auf das Ventilglied 9 ausgeübt, die größer ist als die hydraulische Kraft auf die Druckschulter 13, so daß das Ventilglied 9 mit der Ventildichtfläche 20 am Ventilsitz 22 anliegt und die wenigstens eine Einspritzöffnung 24 gegen die Bohrung 6 abdichtet . Der Einspritzvorgang wird dadurch eingeleitet, daß die hydraulisch erzeugte Schließkraft auf den Ventilkolben 12 so weit reduziert wird, daß sie kleiner ist als die hydraulische Kraft auf die Druckschulter 13 des Ventilgliedes 9. Dadurch erfährt das Ventilglied 9 eine resultierende Kraft, die vom Brennraum weg gerichtet ist, so daß das Ventilglied 9 mit der Ventil - dichtfläche 20 vom Ventilsitz 22 abhebt und die wenigstens eine Einspritzöffnung 24 freigibt. Der Kraftstoff aus dem Druckraum 28 wird nun über die wenigstens eine Einspritzöffnung 24 in den Brennraum der Brennkraftmaschine eingespritzt. Die Einspritzung wird dadurch beendet, daß die hydraulisch erzeugte Schließkraft auf den Ventilkolben 12 so weit erhöht wird, daß die dadurch erzeugte Kraft auf das Ventilglied 9 größer ist als die hydraulische Kraft auf die Druckschulter 13 und die Ventildichtfläche 20. Das Ventilglied 9 wird dadurch wieder mit der Ventildichtfläche 20 gegen den Ventilsitz 22 gepreßt und verschließt so die wenigstens eine Einspritzöffnung 24.The mode of operation of the fuel injection valve is as follows: via the high-pressure fuel source, not shown in the drawing, fuel is introduced into the inlet channel 26, so that a predetermined high level of fuel pressure prevails in the pressure chamber 28 down to the valve seat 22. The pressure of the fuel in the pressure chamber 28 results in a force acting in the axial direction of the valve member 9 on the pressure shoulder 13, which acts on the valve member 9 away from the combustion chamber. In the closed state of the fuel injection valve, a closing force is exerted on the valve member 9 by the valve piston 12, which is greater than the hydraulic force on the pressure shoulder 13, so that the valve member 9 rests with the valve sealing surface 20 on the valve seat 22 and the at least one injection opening 24 against the hole 6 seals. The injection process is initiated in that the hydraulically generated closing force on the valve piston 12 is reduced to such an extent that it is less than the hydraulic force on the pressure shoulder 13 of the valve member 9. As a result, the valve member 9 experiences a resulting force which is directed away from the combustion chamber is so that the valve member 9 with the valve sealing surface 20 lifts off the valve seat 22 and opens at least one injection opening 24. The fuel from the pressure chamber 28 is now injected into the combustion chamber of the internal combustion engine via the at least one injection opening 24. The injection is ended by increasing the hydraulically generated closing force on the valve piston 12 to such an extent that the force thereby generated on the valve member 9 is greater than the hydraulic force on the Pressure shoulder 13 and the valve sealing surface 20. The valve member 9 is thereby pressed again with the valve sealing surface 20 against the valve seat 22 and thus closes the at least one injection opening 24.

Während des gesamten Öffnungs- und Schließvorgangs und während der Einspritzung herrscht im Druckraum 28 ein vorgegebenes, nahezu konstantes Druckniveau des Kraftstoffs. Aufgrund der hohen Drücke im Druckraum 28, die je nach Anwen- düng einige 10 bis über 100 MPa betragen können, wirken auf das Ventilglied 9 und den Ventilkolben 12 so große Kräfte, daß die Kraft der Feder 15 für die Funktion des Kraftstoffeinspritzventils nur eine untergeordnete Rolle spielt. Die Feder 15 dient hauptsächlich dazu, bei abgeschalteter Brenn- kraftmaschine und damit drucklosem Zustand im Druckraum 28 das Kraftstoffeinspritzventil geschlossen zu halten.During the entire opening and closing process and during the injection, a predetermined, almost constant pressure level of the fuel prevails in the pressure chamber 28. Because of the high pressures in the pressure chamber 28, which, depending on the application, can range from a few 10 to over 100 MPa, forces acting on the valve member 9 and the valve piston 12 are so great that the force of the spring 15 for the function of the fuel injection valve is only a minor one Role play. The spring 15 mainly serves to keep the fuel injection valve closed when the internal combustion engine is switched off and thus in the depressurized state in the pressure chamber 28.

Bei der Fertigung des Ventilkörpers 1 können beide Ventilkörperteile 101 und 201 getrennt voneinander gefertigt wer- den. Hierbei ist darauf zu achten, daß die Abschnitte 106 und 206 der Bohrung 6 in Einbaulage der Ventilkörperteile 101 und 201 genau fluchtend zueinander angeordnet sind. Die Trennebene der beiden Ventilkörperteile 101 und 201 teilt den Druckraum 28. Hierdurch ist es ohne weiteres möglich, die Übergänge vom Druckraum 28 zur Bohrung 6 und den Übergang vom Zulaufkanal 26 zum Druckraum 28 sorgfältig zu runden. Dies ist zum einen notwendig, um Verwirbelungen des Kraftstoffs im Bereich des Druckraums 28 zu verhindern, was eine nicht optimale Funktion des Kraftstoffeinspritzventils zur Folge hätte. Zum anderen vermeidet das Runden scharfeWhen the valve body 1 is manufactured, both valve body parts 101 and 201 can be manufactured separately from one another. It should be ensured here that the sections 106 and 206 of the bore 6 in the installed position of the valve body parts 101 and 201 are exactly aligned with one another. The parting plane of the two valve body parts 101 and 201 divides the pressure chamber 28. This makes it easily possible to carefully round the transitions from the pressure chamber 28 to the bore 6 and the transition from the inlet channel 26 to the pressure chamber 28. On the one hand, this is necessary in order to prevent swirling of the fuel in the area of the pressure chamber 28, which would result in the fuel injector not functioning optimally. On the other hand, rounding avoids sharp

Kerben im Ventilkörper und erhöht damit die Hochdruckfestigkeit.Notches in the valve body and thus increases the high pressure resistance.

Da das Ventilglied 9 nahe dem Ventilsitz 22 durch die radia- le Erweiterung 10 im zweiten Abschnitt 206 der Bohrung 6 ge- führt ist, ist eine exakt symmetrische Lage der Ventildicht - flache 20 bezüglich des Ventilsitzes 22 gegeben. Dadurch werden sämtliche Emspritzoffnungen 24 bei der Offnungshub- bewegung des Ventilgliedes 9 gleichmäßig geöffnet und die Einspritzung des Kraftstoffs m den Brennraum der Brennkraftmaschine erfolgt entsprechend gleichförmig durch alle Einspritzöffnungen 24. Hierdurch ist eine optimale Verbrennung gewährleistet und medrigstmögliche Abgaswerte.Since the valve member 9 near the valve seat 22 through the radial extension 10 in the second section 206 of the bore 6 leads, there is an exactly symmetrical position of the valve seal - flat 20 with respect to the valve seat 22. As a result, all the injection openings 24 are opened uniformly during the opening stroke movement of the valve member 9 and the injection of the fuel m into the combustion chamber of the internal combustion engine takes place correspondingly uniformly through all injection openings 24. This ensures optimal combustion and the lowest possible exhaust gas values.

Es kann auch vorgesehen sein, daß der erfindungsgemäße Ven- tilkörper 1 mit einem Ventilhaltekorper 5 verbunden ist, bei dem die Schließkraft nicht hydraulisch über einen Ventilkol- ben 12 auf das Ventilglied 9 ausgeübt wird, sondern durch eine oder mehrere Federn erzeugt wird. Die Steuerung des Einspritzvorgangs erfolgt m diesem Fall nicht über eine Änderung der Schließkraft auf das Ventilglied 9, sondern bei zumindest annähernd gleichbleibender Schließkraft über eine Druckänderung im Druckraum 28. Bei hohem Kraftstoffdruck öffnet das Ventilglied 9 m der oben beschriebenen Art und Weise die wenigstens eine Einspritzöffnung 24, bei abfallendem Kraftstoffdruck wird es durch die Schließkraft wieder gegen den Ventilsitz 22 gepreßt und die Einspritzöffnungen 24 werden verschlossen.It can also be provided that the valve body 1 according to the invention is connected to a valve holding body 5, in which the closing force is not exerted hydraulically on the valve member 9 via a valve piston 12, but is generated by one or more springs. In this case, the control of the injection process does not take place via a change in the closing force on the valve member 9, but with an at least approximately constant closing force via a pressure change in the pressure chamber 28. At high fuel pressure, the valve member 9 opens the at least one injection opening in the manner described above 24, when the fuel pressure drops, it is pressed against the valve seat 22 again by the closing force and the injection openings 24 are closed.

Es ist schwierig und aufwendig, d e beiden Abschnitte 106 und 206 der Bohrung 6 genau fluchtend m den beiden Ventil - körperteilen 101 und 201 auszubilden. Schon durch eine geringe Desachsierung der Bohrungsabschnitte 106,206 kommt es ohne eine zweite Fuhrung des Ventilglieds 9 zu einer leicht asymmetrischen Lage der Ventildichtflache 20 am VentilsitzIt is difficult and expensive to form the two sections 106 and 206 of the bore 6 exactly in alignment with the two valve body parts 101 and 201. Even a slight roofing of the bore sections 106, 206 results in a slightly asymmetrical position of the valve sealing surface 20 on the valve seat without a second guidance of the valve member 9

22 und damit, falls mehrere Einspritzöffnungen 24 vorgesehen sind, zu einem ungleichen Zufluß von Kraftstoff zu den einzelnen Einspritzöffnungen 24. Durch die zusätzliche zweite Führung des Ventilgliedes 9 m der Bohrung 6 und durch den großen Abstand des dichtend gef hrten Abschnitts des Ventil- gliedes 9 zu dieser zusätzlichen Führung ist das Ventilglied 9 jedoch flexibel genug, um eine geringfügige Desachsierung der beiden Abschnitte 106 und 206 der Bohrung 6 auszugleichen, ohne daß es zu einem Fressen des Ventilgliedes 9 in der Bohrung 6 kommt .22 and thus, if several injection openings 24 are provided, to an uneven inflow of fuel to the individual injection openings 24. Due to the additional second guidance of the valve member 9 m of the bore 6 and the large distance between the sealingly guided section of the valve member 9 to this additional guide, the valve member 9 is flexible enough to compensate for a slight roofing of the two sections 106 and 206 of the bore 6, without causing the valve member 9 to seize in the bore 6.

Alternativ zu der in der Zeichnung gezeigten zusätzlichen Führung des Ventilgliedes 9 kann es auch vorgesehen sein, die Führung nicht durch eine radiale Erweiterung 10 des Ven- tilgliedes 9 auszubilden, sondern durch eine radiale Verengung der Bohrung 6. Auch hier müssen Vorkehrungen getroffen werden, die einen Zufluß des Kraftstoffs aus dem Druckraum 28 zu den Einspritzöffnungen 24 ermöglichen, beispielsweise Ausnehmungen an der radialen Verengung oder am Ventilglied 9 im Bereich der radialen Verengung. As an alternative to the additional guidance of the valve member 9 shown in the drawing, provision can also be made for the guidance not to be formed by a radial widening 10 of the valve member 9, but by a radial narrowing of the bore 6. Here too, precautions must be taken that: allow an inflow of fuel from the pressure chamber 28 to the injection openings 24, for example recesses on the radial constriction or on the valve member 9 in the region of the radial constriction.

Claims

Ansprüche Expectations 1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkorper (1) , m dem eine Bohrung (6) ausgebildet ist, an deren dem Brennraum zugewandten Ende ein Ventil - sitz (22) ausgebildet ist, und mit einem kolbenförmigen1. Fuel injection valve for internal combustion engines with a valve body (1), in which a bore (6) is formed, at the end facing the combustion chamber a valve seat (22) is formed, and with a piston-shaped one Ventilglied (9) , das langsverschiebbar m der Bohrung (6) angeordnet ist, wobei am brennraumseitigen Ende des Ven- t lglieds (9) eine Ventild chtflache (20) ausgebildet ist, welche zur Steuerung wenigstens einer Emspπtz- offnung (24) mit dem Ventilsitz (22) zusammenwirkt, wobei das Ventilglied (9) mit einem ersten Abschnitt (109) m einem brennraumabgewandten ersten Abschnitt (106) der Bohrung (6) dichtend gefuhrt ist, und an welchem Ventilglied (9) durch eine radiale Erweiterung (10) eine weite- re Fuhrung ausgebildet ist, die zwischen dem dichtend geführten ersten Abschnitt (109) des Ventilgliedes (9) und der Ventildichtflache (20) m einem zweiten Abschnitt (206) der Bohrung (6) angeordnet st, und mit einem durch eine radiale Erweiterung der Bohrung (6) gebildeten Druckraum (28) , der am Übergang vom ersten (106) zum zweiten Abschnitt (206) der Bohrung (6) angeordnet ist und m welchen Druckraum (28) ein im Ventilkorper (1) ausgebildeter Zulaufkanal (26) mundet, über den der Druckraum (28) mit Kraftstoff befulibar ist, dadurch ge- kennzeichnet, daß der Ventilkorper (1) aus wenigstens zwei Ventilkorperteilen (101, 201) besteht, wobei der brennraumabgewandte, erste Abschnitt (106) der Bohrung (6) im ersten Ventilkörperteil (101) angeordnet ist und der zweite Abschnitt (206) der Bohrung (6), m dem die radiale Erweiterung (10) des Ventilglieds (9) geführt ist, m einem zweiten Ventilkörperteil (201)Valve member (9), which is arranged to be slowly displaceable in the bore (6), a valve sealing surface (20) being formed at the end of the valve member (9) on the combustion chamber side, which valve surface controls at least one discharge opening (24) with the Valve seat (22) cooperates, the valve member (9) being sealingly guided with a first section (109) in a first section (106) of the bore (6) facing away from the combustion chamber, and on which valve member (9) by a radial extension (10) a further guide is formed which is arranged between the sealingly guided first section (109) of the valve member (9) and the valve sealing surface (20) in a second section (206) of the bore (6), and with one through a radial one Expansion of the bore (6) formed pressure chamber (28), which is arranged at the transition from the first (106) to the second section (206) of the bore (6) and with which pressure chamber (28) an inlet channel (26) formed in the valve body (1) ) mouths over which the Druckr aum (28) can be filled with fuel, characterized in that the valve body (1) consists of at least There are two valve body parts (101, 201), the first section (106) of the bore (6) facing away from the combustion chamber being arranged in the first valve body part (101) and the second section (206) of the bore (6), with which the radial expansion ( 10) of the valve member (9) is guided in a second valve body part (201) 2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das erste Ventilkörperteil (101) gegen das zweite Ventilkörperteil (201) axial verspannt ist.2. Fuel injection valve according to claim 1, characterized in that the first valve body part (101) against the second valve body part (201) is clamped axially. 3. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Trennflache der beiden Ventilkörperteile (101, 201) im Bereich des Druckraums (23) ver- lauft.3. Fuel injection valve according to claim 1, characterized in that the separating surface of the two valve body parts (101, 201) runs in the region of the pressure chamber (23). 4. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß die Bohrung (6) im zweiten Ventilkörperteil (201) einen anderen Durchmesser aufweist als m ersten Ventilkörperteil (101) .4. Fuel injection valve according to claim 2, characterized in that the bore (6) in the second valve body part (201) has a different diameter than m first valve body part (101). 5. Kraftstoffeinspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die weitere Fuhrung des Ventilglieds (9) nahe dem Ventilsitz (22) angeordnet ist.5. Fuel injection valve according to one of the preceding claims, characterized in that the further guidance of the valve member (9) is arranged near the valve seat (22). 6. Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß die radiale Erweiterung im brennraumseitigen Drittel der Bohrung (6) angeordnet ist. 6. Fuel injection valve according to claim 4, characterized in that the radial extension in the combustion chamber side third of the bore (6) is arranged.
PCT/DE2001/001271 2000-04-01 2001-03-29 Fuel injection valve for an internal combustion engine Ceased WO2001075298A1 (en)

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DE2000116426 DE10016426A1 (en) 2000-04-01 2000-04-01 Fuel injection valve for internal combustion engines
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4205744A1 (en) * 1991-02-26 1992-08-27 Nissan Motor Fuel injection valve for IC engine - has ring of nozzles with each nozzle offset from radial line and at equal angles to each other
US5607106A (en) * 1994-08-10 1997-03-04 Cummins Engine Company Low inertia, wear-resistant valve for engine fuel injection systems
WO2001014736A1 (en) * 1999-08-25 2001-03-01 Caterpillar Inc. Ceramic check for a fuel injector

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4205744A1 (en) * 1991-02-26 1992-08-27 Nissan Motor Fuel injection valve for IC engine - has ring of nozzles with each nozzle offset from radial line and at equal angles to each other
DE4205744C2 (en) 1991-02-26 1996-09-19 Nissan Motor Internal combustion engine fuel injector
US5607106A (en) * 1994-08-10 1997-03-04 Cummins Engine Company Low inertia, wear-resistant valve for engine fuel injection systems
WO2001014736A1 (en) * 1999-08-25 2001-03-01 Caterpillar Inc. Ceramic check for a fuel injector

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