EP0597249B1 - Fuel injection arrangement, especially unit injector for an internal combustion engine - Google Patents

Fuel injection arrangement, especially unit injector for an internal combustion engine Download PDF

Info

Publication number
EP0597249B1
EP0597249B1 EP93116228A EP93116228A EP0597249B1 EP 0597249 B1 EP0597249 B1 EP 0597249B1 EP 93116228 A EP93116228 A EP 93116228A EP 93116228 A EP93116228 A EP 93116228A EP 0597249 B1 EP0597249 B1 EP 0597249B1
Authority
EP
European Patent Office
Prior art keywords
tappet
fuel injection
pin
injection device
retention element
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
EP93116228A
Other languages
German (de)
French (fr)
Other versions
EP0597249A1 (en
Inventor
François Agrain
François Rossignol
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 EP0597249A1 publication Critical patent/EP0597249A1/en
Application granted granted Critical
Publication of EP0597249B1 publication Critical patent/EP0597249B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing

Definitions

  • the invention is based on a fuel injection device, in particular a pump nozzle for internal combustion engines, according to the preamble of claim 1.
  • a fuel injection device of this type known from DE-OS 39 43 419
  • a pump piston axially guided in a cylinder bore of a pump housing is driven back and forth by a cam drive.
  • the pump piston with its end facing away from the cam drive, delimits a pump working chamber in the cylinder bore into which a fuel line opens and which is connected via a pressure channel to an injection valve which projects into the combustion chamber of the internal combustion engine to be supplied.
  • Both the start of high-pressure delivery of the fuel in the pump work space and thus the start of injection and the amount of fuel to be injected are electrically controlled by the closing time of a solenoid valve arranged in the fuel supply line, depending on the operating parameters of the internal combustion engine to be supplied.
  • the transmission of the drive movement of the cam drive to the pump piston takes place via a tappet pin, which acts on the pump piston via a tappet insert.
  • the tappet insert is arranged in a guide sleeve which slides in a guide tube fixed to the housing and which transmits the restoring force of a spring to the pump piston which is clamped between the guide sleeve and the tappet insert via a coupling part.
  • the tappet pin with its end facing the pump piston is guided and secured in the tappet insert in a relatively complex manner, since the tappet pin is axially secured in the tappet insert in the known pump nozzle via a locking ring which is latched into the tappet and is in an axial position between the end face of the tappet insert and an intermediate sleeve is fixed, the intermediate sleeve in turn being held axially on the tappet pin via a snap ring in the bore of the guide sleeve which guides the tappet pin.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that by using an axial securing element with elastic properties, the tappet bolt can be installed or removed with the securing element inserted, without additional components and disassembly of the pump being necessary, what the Manufacturing and assembly costs significantly reduced.
  • both the connection between the tappet pin and the tappet insert, as well as according to claim 2 the connection between the tappet pin and the transmission member to the camshaft are designed in the manner of a ball joint and, according to claim 3, are advantageously axially secured via an elastic securing element.
  • This elastic deformability of the securing element not only simplifies the assembly of the tappet bolt but also protects the cam drive against mechanical destruction when the pump piston is blocked, since the transmission member is pulled out of the bearing in the tappet bolt in this case.
  • the elastic securing element is advantageously designed as an O-ring, which has both limited deformability and high thermal and mechanical strength.
  • the groove guiding the ring is designed with the necessary radial play in order to ensure that the ring can be easily expanded while the ball pin is being passed through. It is advantageously possible to set the force required for assembly or the independent emergency disengagement of the ball head, both by dimensioning the ring and the groove.
  • the design of the securing element according to claim 11 offers the advantage that an annular groove in the region of the ball socket can be dispensed with, which enables the component carrying it to be shortened.
  • FIG. 1 shows a longitudinal section through part of a pump nozzle, with a schematic representation of the functionally important components adjoining it, in which the position of the tappet piston and its connection to the adjacent components, as well as a first embodiment of its axial securing in the form of a circular snap ring
  • FIG. 2 shows a second embodiment of the axial securing between the tappet pin and a tappet insert connecting it to the pump piston, in which a 0-ring 3 to 6 show further embodiment variants of the snap ring shown in FIG. 1, FIG.
  • FIG. 7 shows an exemplary embodiment in which the connection between the tappet pin and a rocker arm pin driving it is axially secured via a locking ring, which is guided in an annular groove of the tappet pin and
  • FIG. 8 shows a further exemplary embodiment analogous to FIG. 7, in which the axial securing between the rocker arm pin and the tappet pin takes place via one or more molded sheet metal parts pushed onto the tappet pin gt.
  • a pump piston 1 is guided axially in a cylinder bore 3 of a pump housing 5 and delimits a pump work chamber 7 with its end face there. With its end facing away from the pump work chamber 7, the pump piston 1 projects into a plunger 9, which is connected to a rocker arm 11 of a cam drive, not shown, via which the pump piston 1 is moved axially back and forth.
  • the pump work chamber 7 is connected via a pressure line 13 to an injection valve 15 which projects into the combustion chamber of the internal combustion engine to be supplied and which is arranged in the pump housing 5 and which opens and retracts against the force of a spring when the injection pressure in the pump work chamber 7 and the pressure line 13 is reached Falling below this injection pressure closes.
  • a fuel line 17 opens into it, which starts from a fuel reservoir 19 and in which a fuel feed pump 21 and a magnetically controlled changeover valve 23 are arranged.
  • the changeover valve 23 is controlled as a function of the operating parameters of the internal combustion engine and regulates the beginning and the end of the high-pressure delivery via its opening or closing.
  • the plunger assembly 9 driving the pump piston 1 consists of a plunger pin 25 which acts axially on the pump piston 1 via a cylindrical plunger insert 27 inserted into a plunger sleeve 35 and which is actuated by the rocker arm 11 on its end face remote from the plunger insert 27.
  • the pump piston 1 has, at its end facing away from the pump working space 7, a head piece 31, which is formed by a ring recess 29 and projects into the plunger sleeve 35, with which it projects into a bore 33 in the plunger insert 27 and with its end face it bears against the plunger insert 27.
  • the plunger insert 27 is guided in the plunger sleeve 35, which in turn is axially slidably guided in a bore 37 of a pipe socket 38 of the pump housing 5 that runs coaxially to the cylinder bore 3 and that has an inwardly angled area 39 on its end face facing the pump piston 1, which has one Blind hole with passage opening for the head piece 31 forms.
  • the tappet sleeve 35 has an eccentric bore 47 in the angled region 39 through which the head 31 of the pump piston 1 is threaded into the tappet sleeve 35 during the preassembly of the tappet 9 and then through the bore 33 of the plunger insert 27 is fixed in the middle and thus in contact with the angled area 39.
  • the tappet sleeve 35 has an elongated hole 49 in which a ball 51, which is guided in an annular groove 53 in the bore 37, is arranged.
  • the tappet sleeve 35 widens to form a flange 41 on which a return spring 43 engages, which surrounds the tappet sleeve 35 and the pipe socket 38 and, on the other hand, is supported on a housing shoulder 45 of the pump housing 5.
  • the restoring spring 43 thus counteracts the tappet movement in the direction of the pump working space 7 via the tappet sleeve 35 and brings the pump piston 1 coupled to the tappet sleeve 35 into its initial position during its suction stroke and returning tappet 9, i.e. top dead center.
  • the plunger pin 25 has, on its side facing the pump piston 1, a ball head 55 with a partial spherical surface facing away from the pump piston 1 and ending at the shaft of the plunger pin 25, with the end face of which ball-like over an angular range of a maximum of 180 ° in one on the front side of the plunger insert 27 molded ball socket 57 is mounted.
  • Axial securing of the tappet pin 25 against slipping out in the unloaded, unpressurized state at the end of the pump piston outward movement takes place in this exemplary embodiment via a circular locking ring 59, which is mounted on the side of the ball head 55 facing away from the tappet insert 27 in an annular groove 61 in the tappet sleeve 35 that he can widen when pulling out the tappet pin 25 with a certain force to the extent of the outer diameter of the ball head 55.
  • the plunger pin 25 has a ball socket 63 in which one is analogous to the ball head 55 spherical head 65 of a larger diameter compared to the shaft of a rocker arm bolt 67 screwed vertically into the rocker arm 11 is mounted.
  • the ball head 63 of the rocker arm pin 67 is also axially secured via a circular elastic locking ring 59, which engages behind the ball head 65 via a crimped sheet metal sleeve 69, which was pushed onto the rocker arm pin 67 on the rocker arm pin 67 before the rocker arm pin 67 was installed, and so in Holds on the ball socket 63, the sheet metal sleeve 69 is axially secured via a plurality of pronounced spring tongues 73 distributed over the circumference, which engage in a groove 75 on the outer circumference of the ball socket 63.
  • the exemplary embodiment shown in FIG. 2 differs from that of FIG. 1 only in the type of axial securing of the tappet pin 25 in the tappet sleeve 35.
  • the securing element is formed here by an O-ring 77 with elastic properties (eg Vitton ring), which is guided in a semicircular or rectangular annular groove 61 in cross-section so that it can expand under a certain force to the size of the outer diameter of the ball head 55, so that a simple assembly of the plunger pin 25 in the plunger insert 27 is possible.
  • FIGS. 3 to 6 show different exemplary embodiments of the locking rings 59, wherein in FIG. 3 this is an open wire spring ring bent in the form of a 5-surface closed polygon train, the outer diameter D1 of which is equal to the basic groove diameter and the inner diameter D2 is smaller than the outer diameter of the ball head 55, 65 is.
  • About the wire stiffness of the circular wire can be the Change the assembly or disassembly force of the tappet pin 25.
  • the leg is shortened at the gap b, in order to avoid an overlap of the legs during assembly and, in connection with this, to avoid increased assembly effort.
  • the snap ring shown in FIG. 5 has four legs and transitions in the form of a segment of a circle between them, which increase its rigidity.
  • FIG. 6 shows a 3-leg snap ring with transitions in the shape of a segment of a circle, the inside and outside diameters of which are dimensioned analogously to FIG. 3, but the large gap dimension b of which allows very simple assembly with high elasticity against expansion.
  • the circular-arc-shaped transitions between the individual legs enable a secure guidance of the locking rings 59 in the groove receiving them due to their larger contact surface on the outer diameter compared to edge transitions.
  • FIGS. 7 and 8 show further exemplary embodiments of the axial securing of the rocker arm pin 67 on the tappet pin 25, the securing ring 59 in FIG. 7 being guided directly in a groove 81 in the tappet pin 25.
  • the rocker pin 67 is axially secured via a shaped sheet metal part 81 designed as an annular sleeve, which is locked onto the tappet pin via locking elements (73) designed as spring tongues that engage in a groove 75 on the outer circumference of the head of the ball socket 63 is and the upper, protruding beyond the tappet pin 25 end piece 83 is angled so that it engages behind the ball head 65 of the rocker arm pin 67 and thus secures it against axial slipping out of the pan 63.
  • locking elements (73) designed as spring tongues that engage in a groove 75 on the outer circumference of the head of the ball socket 63 is and the upper, protruding beyond the tappet pin 25 end piece 83 is angled so that it engages behind the ball head 65 of the rocker arm pin 67 and thus secures it against axial slipping out of the pan 63.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einer solchen aus der DE-OS 39 43 419 bekannten Kraftstoffeinspritzeinrichtung dieser Art, wird ein in einer Zylinderbohrung eines Pumpengehäuses axial geführter Pumpenkolben von einem Nockenantrieb hin- und hergehend angetrieben. Der Pumpenkolben begrenzt mit seiner dem Nockenantrieb abgewandten Stirnseite einen Pumpenarbeitsraum in der Zylinderbohrung, in den eine Kraftstoffleitung mündet und der über einen Druckkanal mit einem in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventil verbunden ist. Dabei wird sowohl der Beginn der Hochdruckförderung des im Pumpenarbeitsraum befindlichen Kraftstoffes und somit der Einspritzbeginn als auch die einzuspritzende Kraftstoffmenge durch die Schließzeit eines in der Kraftstoffzuführleitung angeordneten Magnetventils, in Abhängigkeit von Betriebsparametern der zu versorgenden Brennkraftmaschine elektrisch gesteuert.The invention is based on a fuel injection device, in particular a pump nozzle for internal combustion engines, according to the preamble of claim 1. In such a fuel injection device of this type known from DE-OS 39 43 419, a pump piston axially guided in a cylinder bore of a pump housing is driven back and forth by a cam drive. The pump piston, with its end facing away from the cam drive, delimits a pump working chamber in the cylinder bore into which a fuel line opens and which is connected via a pressure channel to an injection valve which projects into the combustion chamber of the internal combustion engine to be supplied. Both the start of high-pressure delivery of the fuel in the pump work space and thus the start of injection and the amount of fuel to be injected are electrically controlled by the closing time of a solenoid valve arranged in the fuel supply line, depending on the operating parameters of the internal combustion engine to be supplied.

Die Übertragung der Antriebsbewegung des Nockenantriebs auf den Pumpenkolben erfolgt dabei über einen Stößelbolzen, der über einen Stößeleinsatz auf den Pumpenkolben wirkt. Der Stößeleinsatz ist in einer Führungshülse angeordnet, die in einem gehäusefesten Führungsrohr gleitet und die die Rückstellkraft einer Feder auf den Pumpenkolben überträgt, der über ein Kupplungsteil zwischen der Führungshülse und dem Stößeleinsatz eingespannt ist.The transmission of the drive movement of the cam drive to the pump piston takes place via a tappet pin, which acts on the pump piston via a tappet insert. The tappet insert is arranged in a guide sleeve which slides in a guide tube fixed to the housing and which transmits the restoring force of a spring to the pump piston which is clamped between the guide sleeve and the tappet insert via a coupling part.

Dabei ist der Stößelbolzen mit seinem dem Pumpenkolben zugewandten Ende relativ aufwendig im Stößeleinsatz geführt und gesichert, da die axiale Sicherung des Stößelbolzens im Stößeleinsatz in der bekannten Pumpedüse über einen im Stößel eingerasteten Sicherungsring erfolgt, der zwischen der Stirnseite des Stößeleinsatzes und einer Zwischenhülse in axialer Lage fixiert wird, wobei die Zwischenhülse ihrerseits über einen Sprengring in der den Stößelbolzen führenden Bohrung der Führungshülse axial am Stößelbolzen gehalten wird.The tappet pin with its end facing the pump piston is guided and secured in the tappet insert in a relatively complex manner, since the tappet pin is axially secured in the tappet insert in the known pump nozzle via a locking ring which is latched into the tappet and is in an axial position between the end face of the tappet insert and an intermediate sleeve is fixed, the intermediate sleeve in turn being held axially on the tappet pin via a snap ring in the bore of the guide sleeve which guides the tappet pin.

Diese aufwendige axiale Sicherung des Stößelbolzens im Stößeleinsatz hat zur Folge, daß die Fertigung und Montage sehr aufwendig ist. Zudem führt diese im Betriebszustand der Pumpe unlösbare Verbindung zwischen dem Stößelbolzen und dem Pumpenkolben unvermeidbar zur Zerstörung des Nockenantriebs im Falle eines Kolbenfressers, d.h. eines Blockierens des Pumpenkolbens.This complex axial securing of the tappet bolt in the tappet insert has the consequence that the manufacture and assembly is very complex. In addition, this inseparable connection between the tappet pin and the pump piston in the operating state of the pump inevitably leads to the destruction of the cam drive in the event of a piston seizure, i.e. blockage of the pump piston.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch die Verwendung eines axialen Sicherungselementes mit elastischen Eigenschaften, der Stößelbolzen bei eingesetztem Sicherungselement ein- oder ausgebaut werden kann, ohne daß weitere Bauteile und eine Demontage der Pumpe nötig sind, was den Fertigungs- und Montageaufwand erheblich senkt.The fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that by using an axial securing element with elastic properties, the tappet bolt can be installed or removed with the securing element inserted, without additional components and disassembly of the pump being necessary, what the Manufacturing and assembly costs significantly reduced.

Die Verwendung einer kugelgelenkartigen Verbindung bringt zudem den Vorteil, daß ein Ausgleich von Fluchtungsabweichungen zwischen der Längsstellung des Stößelbolzens zum Pumpenkolben möglich wird, ohne daß Funktionsstörungen auftreten. Um diesen beschriebenen Effekt konsequent zu nutzen ist dabei sowohl die Verbindung zwischen Stößelbolzen und Stößeleinsatz, als auch gemäß Anspruch 2, die Verbindung zwischen Stößelbolzen und Übertragungsglied zur Nockenwelle kugelgelenkartig ausgeführt und gemäß Anspruch 3 in vorteilhafter Weise über ein elastische Sicherungselement axial gesichert. Diese elastische Verformbarkeit des Sicherungselementes vereinfacht dabei nicht nur die Montage des Stößelbolzens sondern schützt zudem den Nockenantrieb bei blockiertem Pumpenkolben vor einer mechanischen Zerstörung, da das Übertragungsglied in dem Fall aus der Lagerung im Stößelbolzen herausgezogen wird.The use of a ball joint-like connection also has the advantage that a compensation of misalignments between the longitudinal position of the tappet pin to the pump piston is possible without malfunctions occurring. In order to consistently use this described effect, both the connection between the tappet pin and the tappet insert, as well as according to claim 2, the connection between the tappet pin and the transmission member to the camshaft are designed in the manner of a ball joint and, according to claim 3, are advantageously axially secured via an elastic securing element. This elastic deformability of the securing element not only simplifies the assembly of the tappet bolt but also protects the cam drive against mechanical destruction when the pump piston is blocked, since the transmission member is pulled out of the bearing in the tappet bolt in this case.

Dabei ist es gemäß den Ansprüchen 1 bis 3 besonders vorteilhaft die kugelgelenkartige Verbindung jeweils durch einen Kugelkopf, der in einer Gelenkpfanne geführt ist zu bilden, wobei dieser dort über einen Winkel von maximal 180° anliegen sollte um ein problemloses Einsetzen und Herausziehen des Kugelkopfes in die Kugelpfanne zu gewährleisten. Die axiale Sicherung wird dabei wie bereits erwähnt über ein Sicherungselement mit elastischen Eigenschaften gewährleistet, wobei dieses Sicherungselement, das jeweils auf der der Kugelpfanne abgewandten Seite des Kugelbolzens in Anlage an diesen bringbar ist, in Abhängigkeit von seiner Gestaltung so dehnbar ist, daß der jeweilige Kugelbolzen unter Aufbringung einer bestimmten Kraft hindurchführbar ist.It is particularly advantageous in accordance with claims 1 to 3 to form the ball-joint-like connection in each case by a ball head which is guided in a joint socket, which should rest there over an angle of at most 180 ° in order to ensure that the ball head can be inserted and pulled out without problems To ensure ball socket. As already mentioned, the axial securing is ensured by a securing element with elastic properties, this securing element, which can be brought into contact with the ball socket on the side of the ball socket facing away from it, depending on its design, is so extensible that the respective ball pin can be passed through with the application of a certain force.

Das elastische Sicherungselement ist in einem ersten Ausführungsbeispiel gemäß Anspruch 4 in vorteilhafter Weise als O-Ring ausgeführt, der sowohl eine begrenzte Verformbarkeit als auch eine hohe thermische und mechanische Festigkeit aufweist.In a first exemplary embodiment, the elastic securing element is advantageously designed as an O-ring, which has both limited deformability and high thermal and mechanical strength.

Die Auslegung der den Ring führenden Nut erfolgt dabei mit dem erforderlichen radialen Spiel, um ein problemloses Aufweiten des Ringes während des Durchführens des Kugelbolzens zu sichern. Dabei ist es in vorteilhafter Weise möglich sowohl über die Dimensionierung des Ringes, als auch der Nut die für die Montage, bzw. das selbständige Notausrasten des Kugelkopfes nötige Kraft einzustellen.The groove guiding the ring is designed with the necessary radial play in order to ensure that the ring can be easily expanded while the ball pin is being passed through. It is advantageously possible to set the force required for assembly or the independent emergency disengagement of the ball head, both by dimensioning the ring and the groove.

Die in den Ansprüchen 5 bis 10 genannten Ausführungsformen von Sprengringen haben den Vorteil, daß sie als handelsübliche Bauteile leicht und mit geringen Kosten beziebar sind, wobei die Verwendung von kreisförmigen Federdraht die elastischen Eigenschaften dieser Sprengringe noch verstärkt.The embodiments of snap rings mentioned in claims 5 to 10 have the advantage that they are easy to obtain as commercially available components and at low cost, the use of circular spring wire further enhancing the elastic properties of these snap rings.

Die Ausgestaltung des Sicherungselements gemäß Anspruch 11, bietet den Vorteil, daß auf eine Ringnut im Bereich der Kugelpfanne verzichtet werden kann, was eine Verkürzung des diese tragenden Bauteils ermöglicht.The design of the securing element according to claim 11 offers the advantage that an annular groove in the region of the ball socket can be dispensed with, which enables the component carrying it to be shortened.

Um die erfindungsgemäße Kraftstoffeinspritzeinrichtung direkt von der Nockenwelle der zu versorgenden Brennkraftmaschine anzutreiben wird deren Bewegung in vorteilhafter Weise gemäß Anspruch 12 von einem Kipphebel auf den Stößelbolzen übertragen.In order to drive the fuel injection device according to the invention directly from the camshaft of the internal combustion engine to be supplied, its movement is advantageously transmitted from a rocker arm to the tappet pin according to claim 12.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be found in the drawing, the description and the claims.

Zeichnungdrawing

Acht Ausführungsbeispiele des Gegenstandes der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher erläutert. Es zeigen die Figur 1 einen Längsschnitt durch einen Teil einer Pumpedüse, mit schematischer Darstellung der daran angrenzenden funktionswichtigen Bauelemente, in der die Lage des Stößelkolbens und seine Verbindung mit den angrenzenden Bauteilen, sowie ein erstes Ausführungsbeispiel seiner axialen Sicherung in Form eines kreisförmigen Sprengringes dargestellt ist, die Figur 2 ein zweites Ausführungsbeispiel der axialen Sicherung zwischen dem Stößelbolzen und einem diesen mit dem Pumpenkolben verbindenden Stößeleinsatz, bei dem ein 0-Ring in die Bohrung der den Stößeleinsatz führenden Stößelhülse eingesetzt ist, die Figuren 3 bis 6 weitere Ausführungsvarianten des in Figur 1 dargestellten Sprengringes, die Figur 7 ein Ausführungsbeispiel bei dem die axiale Sicherung der Verbindung zwischen dem Stößelbolzen und einem diesen antreibenden Kipphebelbolzen über einen Sicherungsring erfolgt, der in einer Ringnut des Stößelbolzens geführt wird und die Figur 8 ein weiteres Ausführungsbeispiel analog zur Figur 7, bei dem die axiale Sicherung zwischen Kipphebelbolzen und Stößelbolzen über ein bzw. mehrere auf den Stößelbolzen aufgeschobene Formblechteile erfolgt.Eight embodiments of the object of the invention are shown in the drawing and are explained in more detail below. FIG. 1 shows a longitudinal section through part of a pump nozzle, with a schematic representation of the functionally important components adjoining it, in which the position of the tappet piston and its connection to the adjacent components, as well as a first embodiment of its axial securing in the form of a circular snap ring, FIG. 2 shows a second embodiment of the axial securing between the tappet pin and a tappet insert connecting it to the pump piston, in which a 0-ring 3 to 6 show further embodiment variants of the snap ring shown in FIG. 1, FIG. 7 shows an exemplary embodiment in which the connection between the tappet pin and a rocker arm pin driving it is axially secured via a locking ring, which is guided in an annular groove of the tappet pin and FIG. 8 shows a further exemplary embodiment analogous to FIG. 7, in which the axial securing between the rocker arm pin and the tappet pin takes place via one or more molded sheet metal parts pushed onto the tappet pin gt.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der in der Figur 1 dargestellten und nur in ihren erfindungswesentlichen Bereichen beschriebenen Pumpedüse ist ein Pumpenkolben 1 axial in einer Zylinderbohrung 3 eines Pumpengehäuses 5 geführt und begrenzt mit seiner Stirnseite dort einen Pumpenarbeitsraum 7. Mit seinem dem Pumpenarbeitsraum 7 abgewandten Ende ragt der Pumpenkolben 1 in einen Stößel 9, der mit einem Kipphebel 11 eines nicht näher dargestellten Nockenantriebs verbunden ist, über den der Pumpenkolben 1 axial hin- und herbewegt wird. Der Pumpenarbeitsraum 7 ist über eine Druckleitung 13 mit einem, in den Brennraum der zu versorgenden Brennkraftmaschine ragenden, im Pumpengehäuse 5 angeordneten Einspritzventil 15 verbunden, das beim Erreichen eines bestimmten Einspritzdrucks im Pumpenarbeitsraum 7 und der Druckleitung 13 entgegen der Kraft einer Feder öffnet und nach Absinken unter diesen Einspritzdruck schließt.In the pump nozzle shown in FIG. 1 and described only in its areas essential to the invention, a pump piston 1 is guided axially in a cylinder bore 3 of a pump housing 5 and delimits a pump work chamber 7 with its end face there. With its end facing away from the pump work chamber 7, the pump piston 1 projects into a plunger 9, which is connected to a rocker arm 11 of a cam drive, not shown, via which the pump piston 1 is moved axially back and forth. The pump work chamber 7 is connected via a pressure line 13 to an injection valve 15 which projects into the combustion chamber of the internal combustion engine to be supplied and which is arranged in the pump housing 5 and which opens and retracts against the force of a spring when the injection pressure in the pump work chamber 7 and the pressure line 13 is reached Falling below this injection pressure closes.

Zur Versorgung des Pumpenarbeitsraumes 7 mit Kraftstoff mündet eine Kraftstoffleitung 17 in diesen, die von einem Kraftstoffvorratsbehälter 19 ausgeht und in der eine Kraftstofförderpumpe 21 sowie ein magnetgesteuertes Umschaltventil 23 angeordnet sind. Das Umschaltventil 23 wird dabei in Abhängigkeit von Betriebsparametern der Brennkraftmaschine angesteuert und regelt über sein Öffnen bzw. Schließen den Beginn und das Ende der Hochdruckförderung.To supply the pump work space 7 with fuel, a fuel line 17 opens into it, which starts from a fuel reservoir 19 and in which a fuel feed pump 21 and a magnetically controlled changeover valve 23 are arranged. The changeover valve 23 is controlled as a function of the operating parameters of the internal combustion engine and regulates the beginning and the end of the high-pressure delivery via its opening or closing.

Der den Pumpenkolben 1 antreibende Stößelverband 9 besteht aus einem Stößelbolzen 25, der über einen zylinderförmigen, in eine Stößelhülse 35 eingesetzten Stößeleinsatz 27 axial auf den Pumpenkolben 1 wirkt und der auf seiner dem Stößeleinsatz 27 abgewandten Stirnseite vom Kipphebel 11 beaufschlagt wird. Der Pumpenkolben 1 weist dazu an seinem dem Pumpenarbeitsraum 7 abgewandten Ende ein durch einen Ringeinstich 29 entstandenes, in die Stößelhülse 35 hineinragendes Kopfstück 31 auf, mit dem er in eine Bohrung 33 des Stößeleinsatzes 27 ragt und mit dessen Stirnseite er am Stößeleinsatz 27 anliegt. Der Stößeleinsatz 27 ist in der Stößelhülse 35 geführt, die ihrerseits gleitend in einer koaxial zur Zylinderbohrung 3 verlaufenden Bohrung 37 eines Rohrstutzens 38 des Pumpengehäuses 5 axial geführt ist und die auf ihrer dem Pumpenkolben 1 zugewandten Stirnseite einen nach innen abgewinkelten Bereich 39 aufweist, der eine Sackbohrung mit Durchtrittsöffnung für das Kopfstück 31 bildet. Um eine Montage des Pumpenkolbens 1 in die Stößelhülse 35 zu ermöglichen, weist die Stößelhülse 35 im abgewinkelten Bereich 39 eine exzentrische Bohrung 47 auf, durch die der Kopf 31 des Pumpenkolbens 1 bei der Vormontage des Stößels 9 in die Stößelhülse 35 eingefädelt und im Anschluß durch die Bohrung 33 des Stößeleinsatzes 27 in der Mitte und damit in Anlage am abgewinkelten Bereich 39 fixiert wird.The plunger assembly 9 driving the pump piston 1 consists of a plunger pin 25 which acts axially on the pump piston 1 via a cylindrical plunger insert 27 inserted into a plunger sleeve 35 and which is actuated by the rocker arm 11 on its end face remote from the plunger insert 27. For this purpose, the pump piston 1 has, at its end facing away from the pump working space 7, a head piece 31, which is formed by a ring recess 29 and projects into the plunger sleeve 35, with which it projects into a bore 33 in the plunger insert 27 and with its end face it bears against the plunger insert 27. The plunger insert 27 is guided in the plunger sleeve 35, which in turn is axially slidably guided in a bore 37 of a pipe socket 38 of the pump housing 5 that runs coaxially to the cylinder bore 3 and that has an inwardly angled area 39 on its end face facing the pump piston 1, which has one Blind hole with passage opening for the head piece 31 forms. In order to enable assembly of the pump piston 1 in the tappet sleeve 35, the tappet sleeve 35 has an eccentric bore 47 in the angled region 39 through which the head 31 of the pump piston 1 is threaded into the tappet sleeve 35 during the preassembly of the tappet 9 and then through the bore 33 of the plunger insert 27 is fixed in the middle and thus in contact with the angled area 39.

Zur Verdrehsicherung und axialen Hubbegrenzung der Stößelhülse 35 in der Bohrung 37 des Pumpengehäuses 5, weist die Stößelhülse 35 ein Langloch 49 auf, in dem eine Kugel 51, die in einer Ringnut 53 der Bohrung 37 geführt ist, angeordnet ist.To prevent rotation and to limit the axial stroke of the tappet sleeve 35 in the bore 37 of the pump housing 5, the tappet sleeve 35 has an elongated hole 49 in which a ball 51, which is guided in an annular groove 53 in the bore 37, is arranged.

An ihrem dem Pumpenkolben 1 abgewandten Ende erweitert sich die Stößelhülse 35 unter Bildung eines Flansches 41 an dem eine Rückstellfeder 43 angreift, die die Stößelhülse 35 und den Rohrstutzen 38 umschließt und sich andererseits an einem Gehäuseabsatz 45 des Pumpengehäuses 5 abstützt. Die Rückstellfeder 43 wirkt somit über die Stößelhülse 35 der Stößelbewegung in Richtung Pumpenarbeitsraum 7 entgegen und bringt den mit der Stößelhülse 35 gekoppelten Pumpenkolben 1 bei seinem Saughub und zurücklaufenden Stößel 9 in seine Ausgangslage, d.h. den oberen Totpunkt zurück.At its end facing away from the pump piston 1, the tappet sleeve 35 widens to form a flange 41 on which a return spring 43 engages, which surrounds the tappet sleeve 35 and the pipe socket 38 and, on the other hand, is supported on a housing shoulder 45 of the pump housing 5. The restoring spring 43 thus counteracts the tappet movement in the direction of the pump working space 7 via the tappet sleeve 35 and brings the pump piston 1 coupled to the tappet sleeve 35 into its initial position during its suction stroke and returning tappet 9, i.e. top dead center.

Der Stößelbolzen 25 weist auf seiner dem Pumpenkolben 1 zugewandten Seite einen Kugelkopf 55 mit ciner dem Pumpenkolben 1 abgewandten, am Schaft des Stößelbolzens 25 endenden Teilkugelfläche auf, mit dessen Stirnseite er kugelgelenkartig über einen Winkelbereich von maximal 180° in einer auf der Stirnseite des Stößeleinsatzes 27 eingeformten Kugelpfanne 57 gelagert ist. Eine axiale Sicherung des Stößelbolzens 25 gegen ein Herausrutschen im entlasteten drucklosen Zustand am Ende der Pumpenkolbenauswärtsbewegung erfolgt dabei in diesem Ausführungsbeispiel über einen kreisförmigen Sicherungsring 59, der so auf der dem Stößeleinsatz 27 abgewandten Seite des Kugelkopfes 55 in einer Ringnut 61 in der Stößelhülse 35 gelagert ist, daß er sich beim Herausziehen des Stößelbolzens 25 mit einer bestimmten Kraft bis auf das Maß des Außendurchmessers des Kugelkopfes 55 aufweiten kann.The plunger pin 25 has, on its side facing the pump piston 1, a ball head 55 with a partial spherical surface facing away from the pump piston 1 and ending at the shaft of the plunger pin 25, with the end face of which ball-like over an angular range of a maximum of 180 ° in one on the front side of the plunger insert 27 molded ball socket 57 is mounted. Axial securing of the tappet pin 25 against slipping out in the unloaded, unpressurized state at the end of the pump piston outward movement takes place in this exemplary embodiment via a circular locking ring 59, which is mounted on the side of the ball head 55 facing away from the tappet insert 27 in an annular groove 61 in the tappet sleeve 35 that he can widen when pulling out the tappet pin 25 with a certain force to the extent of the outer diameter of the ball head 55.

An dem aus dem Stößel 9 herausragenden Ende weist der Stößelbolzen 25 eine Kugelpfanne 63 auf in der ein analog zum Kugelkopf 55 mit gegenüber dem Schaft vergrößertem Kugeldurchmesser ausgeführter Kugelkopf 65 eines senkrecht in den Kipphebel 11 eingeschraubten Kipphebelbolzens 67 gelagert ist. Der Kugelkopf 63 des Kipphebelbolzens 67 ist dabei ebenfalls über einen kreisförmigen elastischen Sicherungsring 59 axial gesichert, der über eine eingebördelte Blechhülse 69, die vor der Montage des Kipphebelbolzens 67 in den Stößelbolzen 25 auf den Kipphebelbolzen 67 aufgeschoben wurde, den Kugelkopf 65 hintergreift und so in Anlage an der Kugelpfanne 63 hält, wobei die Blechhülse 69 über mehrere über den Umfang verteilte ausgeprägte Federzungen 73, die in eine Nut 75 am Außenumfang der Kugelpfanne 63 angreifen, axial gesichert ist.At the end protruding from the plunger 9, the plunger pin 25 has a ball socket 63 in which one is analogous to the ball head 55 spherical head 65 of a larger diameter compared to the shaft of a rocker arm bolt 67 screwed vertically into the rocker arm 11 is mounted. The ball head 63 of the rocker arm pin 67 is also axially secured via a circular elastic locking ring 59, which engages behind the ball head 65 via a crimped sheet metal sleeve 69, which was pushed onto the rocker arm pin 67 on the rocker arm pin 67 before the rocker arm pin 67 was installed, and so in Holds on the ball socket 63, the sheet metal sleeve 69 is axially secured via a plurality of pronounced spring tongues 73 distributed over the circumference, which engage in a groove 75 on the outer circumference of the ball socket 63.

Das in der Figur 2 gezeigte Ausführungsbeispiel unterscheidet sich zu dem der Figur 1 nur in der Art der axialen Sicherung des Stößelbolzens 25 in der Stößelhülse 35. Das Sicherungselement wird hier durch einen 0-Ring 77 mit elastischen Eigenschaften (z.B. Vitton-Ring) gebildet, der so in einer im Querschnitt halbkreisförmigen oder rechteckigen Ringnut 61 geführt ist, daß er sich unter einer bestimmten Kraft auf das Maß des Außendurchmessers des Kugelkopfes 55 aufweiten kann, so daß eine einfache Montage des Stößelbolzens 25 in den Stößeleinsatz 27 möglich ist.The exemplary embodiment shown in FIG. 2 differs from that of FIG. 1 only in the type of axial securing of the tappet pin 25 in the tappet sleeve 35. The securing element is formed here by an O-ring 77 with elastic properties (eg Vitton ring), which is guided in a semicircular or rectangular annular groove 61 in cross-section so that it can expand under a certain force to the size of the outer diameter of the ball head 55, so that a simple assembly of the plunger pin 25 in the plunger insert 27 is possible.

Die Figuren 3 bis 6 zeigen verschiedene Ausführungsbeispiele der Sicherungsringe 59, wobei dieser in der Figur 3 ein in Form eines 5-flächigen geschlossenen Polygonzuges gebogener offener Drahtfederring ist, dessen Außendurchmesser D1 gleich dem Nutengrunddurchmesser und der Innendurchmesser D2 kleiner als der Außendurchmesser des Kugelkopfes 55, 65 ist. Über die Drahtsteifigkeit des kreisförmigen Drahtes läßt sich dabei die Montage bzw. Demontagekraft des Stößelbolzens 25 verändern.FIGS. 3 to 6 show different exemplary embodiments of the locking rings 59, wherein in FIG. 3 this is an open wire spring ring bent in the form of a 5-surface closed polygon train, the outer diameter D1 of which is equal to the basic groove diameter and the inner diameter D2 is smaller than the outer diameter of the ball head 55, 65 is. About the wire stiffness of the circular wire can be the Change the assembly or disassembly force of the tappet pin 25.

Bei dem in der Figur 4 dargestellte Sprengring ist der Schenkel am Spalt b abgekürzt, um eine Überdeckung der Schenkel bei der Montage und damit verbunden einen erhöhten Montageaufwand zu vermeiden.In the snap ring shown in FIG. 4, the leg is shortened at the gap b, in order to avoid an overlap of the legs during assembly and, in connection with this, to avoid increased assembly effort.

Der in der Figur 5 gezeigte Sprengring weist gegenüber den Figuren 3und 4 vier Schenkel und kreissegmentförmige Übergange dazwischen auf, die dessen Steifigkeit erhöhen.Compared to FIGS. 3 and 4, the snap ring shown in FIG. 5 has four legs and transitions in the form of a segment of a circle between them, which increase its rigidity.

Das in der Figur 6 gezeigte Ausführungsbeispiel zeigt einen 3-schenkligen Sprengring mit kreissegmentförmigen Übergängen, dessen Innen- und Außendurchmesser analog zur Figur 3 dimensioniert sind, dessen großes Spaltmaß b jedoch eine sehr einfache Montage bei hoher Elastizität gegen Aufweiten zuläßt.The exemplary embodiment shown in FIG. 6 shows a 3-leg snap ring with transitions in the shape of a segment of a circle, the inside and outside diameters of which are dimensioned analogously to FIG. 3, but the large gap dimension b of which allows very simple assembly with high elasticity against expansion.

Die kreisbogenförmigen Übergänge zwischen den einzelnen Schenkeln ermöglichen dabei durch ihre gegenüber Kantenübergängen größere Anlagefläche am Außendurchmesser eine sichere Führung der Sicherungsringe 59 in der sie aufnehmenden Nut.The circular-arc-shaped transitions between the individual legs enable a secure guidance of the locking rings 59 in the groove receiving them due to their larger contact surface on the outer diameter compared to edge transitions.

Die Figuren 7 und 8 zeigen weitere Ausführungsbeispiele der axialen Sicherung des Kipphebelbolzens 67 am Stößelbolzen 25, wobei der Sicherungsring 59 in der Figur 7 direkt in einer Nut 81 im Stößelbolzen 25 geführt ist.FIGS. 7 and 8 show further exemplary embodiments of the axial securing of the rocker arm pin 67 on the tappet pin 25, the securing ring 59 in FIG. 7 being guided directly in a groove 81 in the tappet pin 25.

Bei dem in der Figur 8 dargestellten Ausführungsbeispiel erfolgt die axiale Sicherung des Kipphebelbolzens 67 über ein als Ringhülse ausgeführtes Formblechteil 81, das über als Federzungen ausgebildete Rastelemente (73), die in eine Nut 75 am Außenumfang des Kopfes der Kugelpfanne 63 angreifen auf dem Stößelbolzen arretiert ist und dessen oberes, über den Stößelbolzen 25 hinausragendes Endstück 83 so abgewinkelt ist, daß es den Kugelkopf 65 des Kipphebelbolzens 67 hintergreift und so diesen gegen ein axiales Herausrutschen aus der Pfanne 63 sichert.In the exemplary embodiment shown in FIG. 8, the rocker pin 67 is axially secured via a shaped sheet metal part 81 designed as an annular sleeve, which is locked onto the tappet pin via locking elements (73) designed as spring tongues that engage in a groove 75 on the outer circumference of the head of the ball socket 63 is and the upper, protruding beyond the tappet pin 25 end piece 83 is angled so that it engages behind the ball head 65 of the rocker arm pin 67 and thus secures it against axial slipping out of the pan 63.

Dabei ist bei der kugelgelenkartigen Verbindung zwischen dem Kipphebelbolzen 67 und dem Stößelbolzen 25, wie auch bei dessen Verbindung mit dem Stößeleinsatz 27 eine umgekehrte Ausführung möglich, bei der die Kugelpfanne am Kipphebelbolzen 67, bzw. der Kugelkopf am Stößeleinsatz 27 angeordnet wäre.In the case of the ball-joint-like connection between the rocker arm pin 67 and the tappet pin 25, as well as in its connection to the tappet insert 27, a reverse design is possible in which the ball socket would be arranged on the rocker arm pin 67 or the ball head on the tappet insert 27.

Mit der erfindungsgemäßen Axialsicherung des Stößelbolzens 25 gegenüber dem Stößeleinsatz 27 und dem Kipphebelbolzen 67 mit verformbaren Sicherungselementen ist somit neben einer Sicherung gegen eine Zerstörung des Stößelantriebs bei einem Blockieren des Pumpenkolbens 1, eine einfache Montage des Stößelbolzens 25 ohne Demontage der gesamten Pumpe möglich, was den Fertigungsaufwand erheblich reduziert.With the axial securing of the tappet pin 25 according to the invention with respect to the tappet insert 27 and the rocker arm pin 67 with deformable securing elements, in addition to securing against destruction of the tappet drive when the pump piston 1 is blocked, simple assembly of the tappet pin 25 is possible without dismantling the entire pump, which is possible Manufacturing effort significantly reduced.

Claims (12)

  1. Fuel injection device in particular a unit fuel injector, for internal combustion engines with a pump plunger (1) which is guided in a cylinder bore (3) arranged in a pump housing (5), is driven axially in reciprocating fashion counter to the force of a return spring (43) by a cam drive and, with one of its ends, the end facing away from the cam drive, delimits a pump working space (7) which is connected by a delivery line (13) to an injection valve (15) and can be filled with fuel by way of a fuel line (17), the cam drive acting on the pump plunger (1) via a tappet pin (25) which is guided by its spherical end, that facing away from the cam drive, in a spherical socket (57) of a tappet insert (27) connected to the pump plunger (1) and is there secured axially by a retention element (59) between the tappet pin (25) and a tappet sleeve (35) - of larger diameter than the tappet stem - at the end of the tappet pin (25) remote from the spherical socket (57), characterized in that the tappet pin (25) has a spherically-headed end (55) with a partially spherical surface which faces away from the tappet insert (27), ends at the stem of the tappet pin (25) and against which an elastic retention element (59) which permits at least a defined residual axial movement of the tappet (25) in the tappet sleeve (35) and is snapped into a recess (61) in the tappet sleeve (35) comes to rest.
  2. Fuel injection device according to Claim 1, characterized in that the tappet pin (25) is connected at its end remote from the pump plunger (1) to a transmission member (67) in the form of a ball joint which is moved by the camshaft.
  3. Fuel injection device according to Claim 2, characterized in that the ball joint comprises a spherical socket (63) and a spherical head (65) behind which the elastic retention element (59), which is held on the spherical socket (63), engages.
  4. Fuel injection device according to Claims 1 and 3, characterized in that the retention element is designed as an O-ring (77) which is guided with a play in an annular groove (61) of semicircular or rectangular cross-section such that, which groove is of a depth such that the said O-ring can expand in its inside diameter to the outside diameter of the spherical head (55).
  5. Fuel injection device according to Claims 1 and 3, characterized in that the retention element is designed as a circular snap ring (59) which is guided in an annular groove (61) dimensioned in such a way that it permits the increase in diameter in the inserted snap ring necessary for the installation of the respective spherical head (55).
  6. Fuel injection device according to Claims 1 and 3, characterized in that the retention element (59) is an open wire-spring ring bent in the form of a 5-sided polygon, the outside diameter D1 of which is equal to the groove-root diameter of the annular groove (61) and the inside diameter D2 of which is smaller than the outside diameter of the spherical head (55).
  7. Fuel injection device according to Claim 6, characterized in that an enlarged gap (b) of defined size is provided between the ends of the wire-spring ring by shortening one limb.
  8. Fuel injection device according to Claims 1 and 3, characterized in that the retention element (59) is an open wire-spring ring bent in the form of a 4-sided polygon, in which the transitions between the sides of the polygon are of circular design.
  9. Fuel injection device according to Claims 1 and 3, characterized in that the retention element (59) is an open wire-spring ring bent in the form of a 3-sided polygon, in which the transitions between the sides of the polygon are of circular design.
  10. Fuel injection device according to Claims 5 to 9, characterized in that the snap ring is formed from a wire of circular cross-section.
  11. Fuel injection device according to Claim 3, characterized in that the retention element is a shaped sheet-metal part (81) which is designed as an annular sleeve, can be latched to the circumferential wall of that part of the tappet pin (25) which forms the spherical socket (63) by means of latching elements (73), and has spring elements (83) which project into the region of insertion of the spherical head (65) into the spherical socket (63).
  12. Fuel injection device according to Claim 2, characterized in that the transmission of the movement between the camshaft and the tappet pin (25) is accomplished by means of a rocker lever (11), into that end of which which faces the tappet pin (25) is screwed a rocker-lever pin (67) which serves as a transmission member and that end of which which acts on the tappet pin (25) is designed as a spherical head (65) which engages in that end of the tappet pin (25) which is designed as a spherical socket (63) to form the said ball joint.
EP93116228A 1992-11-07 1993-10-07 Fuel injection arrangement, especially unit injector for an internal combustion engine Expired - Lifetime EP0597249B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4237682 1992-11-07
DE4237682A DE4237682A1 (en) 1992-11-07 1992-11-07 Fuel injection device, in particular rump nozzle for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0597249A1 EP0597249A1 (en) 1994-05-18
EP0597249B1 true EP0597249B1 (en) 1996-05-22

Family

ID=6472372

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93116228A Expired - Lifetime EP0597249B1 (en) 1992-11-07 1993-10-07 Fuel injection arrangement, especially unit injector for an internal combustion engine

Country Status (4)

Country Link
US (1) US5402764A (en)
EP (1) EP0597249B1 (en)
JP (1) JPH06200854A (en)
DE (2) DE4237682A1 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5435286A (en) * 1994-05-02 1995-07-25 Cummins Engine Company, Inc. Ball link assembly for vehicle engine drive trains
US5682861A (en) * 1996-05-23 1997-11-04 Caterpillar Inc. Fluid seal for cyclic high pressures within a fuel injection
US6688536B2 (en) * 1997-10-22 2004-02-10 Caterpillar Inc Free floating plunger and fuel injector using same
GB2330626A (en) * 1997-10-22 1999-04-28 Caterpillar Inc Tappet retention for a fuel injector
US5878710A (en) * 1998-07-20 1999-03-09 Caterpillar Inc. Fuel injection shutdown system
US6003790A (en) * 1998-10-14 1999-12-21 Ford Global Technologies, Inc. Pre-load mechanism having self-mounting coil spring
US6607149B2 (en) * 2001-12-28 2003-08-19 Robert Bosch Fuel Systems Corporation Follower assembly with retainer clip for unit injector
CN103670857A (en) * 2012-09-25 2014-03-26 上海电装燃油喷射有限公司 Method for assembling O-shaped ring of plunger and barrel assembly in fuel oil injection pump
AT515737B1 (en) * 2014-05-12 2018-06-15 Avl List Gmbh CAMERA DEVICE FOR AN INTERNAL COMBUSTION ENGINE
CN104612874B (en) * 2014-12-10 2017-01-25 重庆福欧机械有限公司 Automatic fine-adjustment mechanism for fuel capacity control over fuel injection pump
CN105422346B (en) * 2015-12-11 2018-03-13 中国北方发动机研究所(天津) Big flow, high rotating speed rotator type high-pressure common rail variable pump plunger matching parts

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA547612A (en) * 1957-10-15 Seifert Richard Fuel injection control system for internal combustion engines
GB191224127A (en) * 1912-10-22 1913-08-21 James Mckechnie Improvements in and relating to the Injection of Liquid Fuel in Internal Combustion Engines.
GB211377A (en) * 1923-04-25 1924-02-21 Philip Boyce Taneborne Improvements in washers for coach bolts
GB375151A (en) * 1930-10-08 1932-06-23 Bernhard Bischof Improvements in or relating to fuel injection pumps for internal combustion engines
US2897805A (en) * 1957-11-08 1959-08-04 Bundy Tubing Co Tubular push rod and method of making same
US4206734A (en) * 1977-12-27 1980-06-10 Cummins Engine Company, Inc. Adjustable timing mechanism for fuel injection system
US4407241A (en) * 1980-12-31 1983-10-04 Cummins Engine Company, Inc. Expandable hydraulic tappet with a variable exit valve
DE3201011A1 (en) * 1982-01-15 1983-07-28 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP
US4531672A (en) * 1983-05-13 1985-07-30 Cummins Engine Company, Inc. Solenoid operated unit injector having distinct timing, metering and injection periods
US4794894A (en) * 1987-03-05 1989-01-03 Cummins Engine Company, Inc. Ceramic tipped pivot rod and method for its manufacture
DE3813320A1 (en) * 1988-04-08 1989-10-19 Voest Alpine Automotive PUMP NOZZLE FOR DIESEL ENGINES
US4864983A (en) * 1988-08-17 1989-09-12 Caterpillar Inc. Pushrod retainer
US4966108A (en) * 1989-04-28 1990-10-30 Cummins Engine Company, Inc. Sintered ceramic ball and socket joint assembly
DE3943419A1 (en) * 1989-12-30 1991-07-04 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES, IN PARTICULAR PUMPEDUESE
GB9026841D0 (en) * 1990-12-11 1991-01-30 Lucas Ind Plc Fuel injection pump
US5320278A (en) * 1993-07-26 1994-06-14 Cummins Engine Company, Inc. High pressure fuel injector with fuel drainage valve

Also Published As

Publication number Publication date
US5402764A (en) 1995-04-04
DE4237682A1 (en) 1994-05-11
DE59302680D1 (en) 1996-06-27
JPH06200854A (en) 1994-07-19
EP0597249A1 (en) 1994-05-18

Similar Documents

Publication Publication Date Title
DE4227853C2 (en) Fuel injection pump for internal combustion engines
EP2812559B1 (en) Fuel injector and apparatus to inject fuel
DE4302668A1 (en) Fuel injection device for internal combustion engines
EP2108080A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
EP0597249B1 (en) Fuel injection arrangement, especially unit injector for an internal combustion engine
DE102009000859A1 (en) Fuel high pressure pump for use as plug-in pump for conveying fuel for common rail fuel injection system of internal combustion engine, has safety ring inserted into annular ring and projecting over annular ring in relaxed condition
WO2018073246A1 (en) Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve
DE69200567T2 (en) Fuel injector.
DE19913680B4 (en) fuel injector
EP1373710A1 (en) Fuel-injection valve for internal combustion engines
DE10139622A1 (en) Fuel injection valve has nozzle body with arrangement corresponding to holding tool for holding nozzle body in defined position with respect to holding body during assembly
EP1490591B1 (en) Device for damping vibrations on fuel injection systems having a high-pressure accumulating space
EP3387247B1 (en) Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve
DE3202405C2 (en) Fuel injection pump for internal combustion engines
DE10121340A1 (en) Common rail injector for internal combustion engine fuel injection system has casing and intermediate plate bounding control chamber implemented in one piece with inlet and outlet choke
DE10304742A1 (en) Fuel injection device for an internal combustion engine
DE10132450A1 (en) Fuel injection valve for internal combustion engines
EP0396127A1 (en) Fuel injection apparatus
WO2016142072A1 (en) High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine
DE4134592C2 (en) Fuel injection pump for an internal combustion engine
DE2150973A1 (en) FUEL INJECTION PUMP FOR COMBUSTION MACHINES
DE4127003A1 (en) ELECTRICALLY CONTROLLED PUMPEDUESE FOR FUEL INJECTION DEVICES IN INTERNAL COMBUSTION ENGINES
DE19908417B4 (en) Control valve for the injection system of a diesel engine
DE102016223960A1 (en) Electromagnetically actuated inlet valve and high-pressure pump with inlet valve
WO2006128754A1 (en) Common rail injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19941118

17Q First examination report despatched

Effective date: 19951114

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59302680

Country of ref document: DE

Date of ref document: 19960627

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960725

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20030930

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20031024

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041007

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20041007

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050630

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20081222

Year of fee payment: 16

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100501