EP0153331B1 - Pump injector for fuel injection of internal combustion engines - Google Patents

Pump injector for fuel injection of internal combustion engines Download PDF

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Publication number
EP0153331B1
EP0153331B1 EP84902788A EP84902788A EP0153331B1 EP 0153331 B1 EP0153331 B1 EP 0153331B1 EP 84902788 A EP84902788 A EP 84902788A EP 84902788 A EP84902788 A EP 84902788A EP 0153331 B1 EP0153331 B1 EP 0153331B1
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EP
European Patent Office
Prior art keywords
pump
piston
internal combustion
injection
cylinder head
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
Application number
EP84902788A
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German (de)
French (fr)
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EP0153331A1 (en
Inventor
Jean Leblanc
François Rossignol
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Priority to AT84902788T priority Critical patent/ATE23209T1/en
Publication of EP0153331A1 publication Critical patent/EP0153331A1/en
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Publication of EP0153331B1 publication Critical patent/EP0153331B1/en
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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
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps

Definitions

  • the invention is based on a pump nozzle according to the generic preamble of the main claim.
  • a pump nozzle of this type is already known (DE-A-32 26 238), in which the piston injection pump and the injection nozzle are combined in a common pump housing to form a structural unit attached to the cylinder head of the internal combustion engine.
  • the design arranged one behind the other is preferably at right angles to the longitudinal axis of the pump piston, also referred to as the line of action of the injection pump, and the longitudinal axis of the injection nozzle. This measure was taken to achieve a compact design and to absorb the pumping forces at a point on the cylinder head that is distant from the location hole for the injection nozzle.
  • the diameter and design of the injection nozzle and the wall thicknesses surrounding this nozzle can be optimally designed in the cylinder head. This is possible because the very high pumping forces, which are of the order of 2000 N, are absorbed at one point on the cylinder head, which can be dimensioned accordingly.
  • the pump nozzle described in FIG. 2 of the aforementioned publication is supported with an end support surface facing away from the camshaft on a corresponding surface of the cylinder head.
  • the injection nozzle which is arranged laterally at an angle to the longitudinal axis of the pump piston, projects into the working cylinder of the internal combustion engine, received by a receiving bore in the cylinder head, and has no transmission and clamping forces to be transmitted.
  • a disadvantage of this arrangement is that the positional tolerances of the support surfaces of the laterally mounted injection nozzle and the receiving bore in the cylinder head must be tolerated extremely tightly so that no clamping and clamping forces can act on the injection nozzle.
  • This is particularly critical because the cylinder head is subject to very large temperature differences and the thermal expansion of the cylinder head and the pump housing lead to deviations in the mounting position in addition to the manufacturing tolerances.
  • the aim of the invention is to intercept the pump forces in the cylinder head in such a way that even with large temperature deviations and the manufacturing tolerances that occur, no forces stressing the injection nozzle can act on them.
  • the outward-facing end face of the opposing piston forming the support bearing on the support bearing transmits the pumping forces emanating from the injection pressure in the pump working chamber directly into the cylinder head without these forces being introduced into the pump housing.
  • the injection nozzle attached to the housing attachment projecting at least approximately at right angles to the longitudinal axis of the pump piston and the associated receiving bore are completely relieved of the pump forces.
  • the pump forces transmitted from the pump piston to the counter-piston via the pressurized fuel are completely introduced into the support bearing.
  • the leakage fuel which is inevitable even with narrow tolerances, is discharged specifically into a leakage fuel line.
  • the spring element which is supported both on the counter-piston and on the pump housing, always provides non-positive support of the counter-piston on the support bearing, which is also effective during the suction stroke of the pump piston, and compensates with its preload force F 2 a corresponding mean preload force F, the plunger spring of the injection pump.
  • FIG. 1 shows the first exemplary embodiment on the basis of a pump nozzle, which is partly shown in longitudinal section and is shown in a highly simplified manner and is built into the cylinder head of the internal combustion engine, and FIG.
  • the pump housing designated 11 receives a piston injection pump 12 and additionally carries a pump pump 13 arranged at right angles to the longitudinal axis A
  • Nete injector 14 of a known type The injection nozzle 14 is connected to this pump work space 15 via a pressure channel 16 opening out laterally from a pump work space 15 and screwed to a housing projection 11 a of the pump housing 11 projecting laterally, at least approximately at right angles to the longitudinal axis A of the pump piston 13.
  • the injection nozzle 14 is inserted into a receiving bore 17 of a cylinder head 18 of the associated internal combustion engine and is fastened to the cylinder head 18 in a manner known per se via clamping claws or stud bolts 19. By means of this fastening, the entire pump nozzle 10 is held in the cylinder head 18, since an additional fastening of the injection pump part is unnecessary due to the inventive design of the pump nozzle 10 described in detail below.
  • the pump piston 13 slidably guided in a pump cylinder 21 is driven by a cam 22a of an engine camshaft 22 of the internal combustion engine with the interposition of a tappet 23 in the stroke direction, i.e. in the direction of its longitudinal axis A, actuates and acts on the pump work space 15.
  • This pump work space 15, which is formed by a section of the pump cylinder 21, is sealed pressure-tight on the one hand by the pump piston 13 and on the other hand by an inner end face 24a of a counter-piston 24 by means of a correspondingly close fit of the associated components.
  • An outward-facing end face 24b of the counter-piston 24 facing away from the inner end face 24a bears against a support bearing 25 under the hydraulic force of the fuel under pressure in the pump work chamber 15 and is therefore also referred to below as a support surface 24b.
  • This support bearing 25 is an integral part of the cylinder head 18 and absorbs the entire pumping or reaction force F, which originates from the pump piston drive and is transferred to the counter piston 24 via the pressurized fuel in the pump working chamber 15, so that the pump housing 11 is largely relieved.
  • the counter-piston 24 which is designed as a floating piston, is fitted in the region of an end section 11b of the pump housing 11 facing away from the motor camshaft 22 into an extension 21a of the pump cylinder 21 which has a constant diameter D up to this end section 11b.
  • the support surface 24b of the counter-piston 24 forms the outermost axial extension of the injection pump 12 in the direction of the longitudinal axis A of the pump piston A.
  • annular grooves 26, 27 and 28, one behind the other are incorporated from the pump work chamber 15, of which the one closest to the pump work chamber 15 is connected as one with a leak fuel line 29 Leak fuel return groove 26 is used.
  • the second annular groove 27 receives a sealing ring 31 which prevents leakage of fuel from escaping to the outside, and a snap ring 32 which forms a radial projection is inserted into the third annular groove 28.
  • the support surface 24b 'on the counter-piston 24' formed by the outward-facing end surface is pressed against the support bearing 25 'under the pretensioning force of a spring element 33 formed in the present example by a plate spring and is supported on the one hand on the radial projection of the counter-piston formed by the snap ring 32 24 'and on the other hand from the end section 11b of the pump housing 11.
  • the support bearing 25 'for the counter-piston 24' is formed by a screw part which is adjustable to adjust its installation position, is screwed into the cylinder head 18 of the internal combustion engine and is secured in position. This allows installation tolerances to be compensated for. The installation of the pump nozzle 10 'is also facilitated when the support bearing 25' is screwed out to the right, and the installation position of the counter-piston 24 'can be adjusted continuously. On the one hand, manufacturing tolerances can be compensated for and, on the other hand, the pretensioning force F 2 of the plate spring 33 can be changed so that it can be made equal to the force denoted by F 1 .
  • F 1 is the mean value of the pretensioning force transmitted from the plunger 23 to a plunger spring 34 during the lifting movements of the pump piston 13 and from this via a flange 35a of a guide sleeve 35 for the plunger 23 to the pump housing 11.
  • the arrows representing the forces F 1 and F 2 have been drawn in outwards for clarity. The purely space-related advantages of the selected design of the pump nozzle 10 'can be seen particularly clearly from FIG.

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

Abstract

Pump injector (10) comprising an injection nozzle (14) mounted at least approximately at right angle with respect to the longitudinal axis (A) on the pump housing (11) of the piston injection pump (12). The injection pump (12) bears with a bearing face (24b) forming the axial end projection thereof on a support bearing (25) provided at the cylinder head (18) of the internal combustion engine. The bearing surface (24b) is formed of a front face directed to the outside, of an opposite piston (24) introduced in the prolongation of the longitudinal axis (A) of the pump piston in the pump cylinder (21) and sealingly closing the pump working chamber (15) by means of an inner front surface (24a). The pump forces on the pressurized fuel in the pump working chamber (15) are thereby taken away from the pump housing (11) and received at the cylinder head at a location remote from a supply inlet (17) for the fuel injection nozzle (14).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Pumpedüse gemäss dem gattungsbildenden Oberbegriff des Hauptanspruchs. Es ist bereits eine Pumpedüse dieser Bauart bekannt (DE-A-32 26 238), bei der Kolbeneinspritzpumpe und Einspritzdüse in einem gemeinsamen Pumpengehäuse zu einer an den Zylinderkopf der Brennkraftmaschine angebauten Baueinheit zusammengefasst sind. Abweichend von der sonst üblichen gleichachsigen, d.h. hintereinander angeordneten Bauweise stehen bei der bekannten Pumpedüse die auch als Wirkungslinie der Einspritzpumpe bezeichnete Längsachse des Pumpenkolbens und die Längsachse der Einspritzdüse in einem vorzugsweise rechten Winkel zueinander. Diese Massnahme wurde getroffen, um eine gedrängte Bauweise zu erreichen und die Pumpkräfte an einer Stelle des Zylinderkopfes abzufangen, die entfernt von der Aufnahmebohrung für die Einspritzdüse liegt. Dies hat den Vorteil, dass Durchmesser und Bauform der Einspritzdüse und die diese Düse umgebenden Wandstärken im Zylinderkopf optimal ausgelegt werden können. Dies ist möglich, weil die sehr hohen, in der Grössenordnung von 2000 N liegenden Pumpkräfte an einer Stelle des Zylinderkopfes abgefangen werden, die entsprechend stark dimensioniert werden kann. Dazu stützt sich die in Figur 2 der vorgenannten Offenlegungsschrift beschriebene Pumpedüse mit einer von der Nockenwelle abgewandten stirnseitigen Abstützfläche an einer entsprechenden Fläche des Zylinderkopfes ab. Die seitlich in einem Winkel zur Pumpenkolbenlängsachse angeordnete Einspritzdüse ragt, von einerAufnahmebohrung im Zylinderkopf aufgenommen, in den Arbeitszylinder der Brennkraftmaschine hinein und hat keine Pump- und Spannkräfte zu übertragen. Nachteilig bei dieser Anordnung ist aber, dass die Lagetoleranzen der Abstützflächen der seitlich angebauten Einspritzdüse und der Aufnahmebohrung im Zylinderkopf äusserst eng toleriert werden müssen, damit keine Spann- und Klemmkräfte auf die Einspritzdüse einwirken können. Dies ist besonders deshalb kritisch, weil der Zylinderkopf sehr grossen Temperaturdifferenzen unterworfen ist und die Wärmedehnungen des Zylinderkopfes und des Pumpengehäuses zusätzlich zu den Fertigungstoleranzen zu Abweichungen in der Anbaulage führen. Ziel der Erfindung ist es nun, die Pumpkräfte so im Zylinderkopf abzufangen, dass auch bei grossen Temperaturabweichungen und den vorkommenden Fertigungstoleranzen keine die Einspritzdüse belastenden Kräfte auf diese einwirken können.The invention is based on a pump nozzle according to the generic preamble of the main claim. A pump nozzle of this type is already known (DE-A-32 26 238), in which the piston injection pump and the injection nozzle are combined in a common pump housing to form a structural unit attached to the cylinder head of the internal combustion engine. Deviating from the otherwise common coaxial, i.e. In the known pump nozzle, the design arranged one behind the other is preferably at right angles to the longitudinal axis of the pump piston, also referred to as the line of action of the injection pump, and the longitudinal axis of the injection nozzle. This measure was taken to achieve a compact design and to absorb the pumping forces at a point on the cylinder head that is distant from the location hole for the injection nozzle. This has the advantage that the diameter and design of the injection nozzle and the wall thicknesses surrounding this nozzle can be optimally designed in the cylinder head. This is possible because the very high pumping forces, which are of the order of 2000 N, are absorbed at one point on the cylinder head, which can be dimensioned accordingly. For this purpose, the pump nozzle described in FIG. 2 of the aforementioned publication is supported with an end support surface facing away from the camshaft on a corresponding surface of the cylinder head. The injection nozzle, which is arranged laterally at an angle to the longitudinal axis of the pump piston, projects into the working cylinder of the internal combustion engine, received by a receiving bore in the cylinder head, and has no transmission and clamping forces to be transmitted. A disadvantage of this arrangement, however, is that the positional tolerances of the support surfaces of the laterally mounted injection nozzle and the receiving bore in the cylinder head must be tolerated extremely tightly so that no clamping and clamping forces can act on the injection nozzle. This is particularly critical because the cylinder head is subject to very large temperature differences and the thermal expansion of the cylinder head and the pump housing lead to deviations in the mounting position in addition to the manufacturing tolerances. The aim of the invention is to intercept the pump forces in the cylinder head in such a way that even with large temperature deviations and the manufacturing tolerances that occur, no forces stressing the injection nozzle can act on them.

Vorteile der ErfindungAdvantages of the invention

Bei der erfindungsgemässen Pumpedüse mit den kennzeichnenden Merkmalen des Hauptanspruchs werden durch den mit seiner nach aussen weisenden Stirnfläche die am Abstützlager anliegende Abstützfläche bildenden Gegenkolben die vom Einspritzdruck im Pumpenarbeitsraum ausgehenden Pumpkräfte direkt in den Zylinderkopf übertragen, ohne dass diese Kräfte in das Pumpengehäuse eingeleitet werden. Damit ist die an den mindestens annähernd rechtwinklig zur Längsachse des Pumpenkolbens vorspringenden Gehäuseansatz angebaute Einspritzdüse und die zugehörige Aufnahmebohrung vollkommen von den Pumpkräften entlastet. So werden bei dem gemäss Anspruch 2 als schwimmender Kolben in eine mit gleichbleibendem Durchmesser bis zum Endabschnitt des Pumpengehäuses durchgeführte Verlängerung des Pumpenzylinders eingepassten Gegenkolben die vom Pumpenkolben über den unter Druck gesetzten Kraftstoff auf den Gegenkolben übertragenen Pumpkräfte vollständig in das Abstützlager eingeleitet. Es ist allerdings auch möglich, durch geringe Durchmesserunterschiede am Pumpenkolben und Gegenkolben mit den entsprechend ausgebildeten Bohrungsabschnitten im Pumpenzylinder eine Druckschulter zu bilden, die zusätzlich, z.B. von der Stösselfeder herrührende, Antriebskräfte kompensiert.In the inventive pump nozzle with the characterizing features of the main claim, the outward-facing end face of the opposing piston forming the support bearing on the support bearing transmits the pumping forces emanating from the injection pressure in the pump working chamber directly into the cylinder head without these forces being introduced into the pump housing. Thus, the injection nozzle attached to the housing attachment projecting at least approximately at right angles to the longitudinal axis of the pump piston and the associated receiving bore are completely relieved of the pump forces. Thus, in the case of the counter-piston fitted as a floating piston into an extension of the pump cylinder having a constant diameter up to the end section of the pump housing, the pump forces transmitted from the pump piston to the counter-piston via the pressurized fuel are completely introduced into the support bearing. However, it is also possible to form a pressure shoulder by means of small diameter differences on the pump piston and counter-piston with the appropriately designed bore sections in the pump cylinder, which shoulder, in addition, e.g. drive forces originating from the plunger spring are compensated.

Weitere vorteilhafte Massnahmen und konstruktive Ausgestaltungen und Verbesserungen sind den Unteransprüchen 3 bis 6 zu entnehmen. So wird durch die kennzeichnenden Merkmale des Anspruchs 3 der auch bei engen Toleranzen unvermeidliche Leckkraftstoff gezielt in eine Leckkraftstoffleitung abgeführt. Das gemäss Anspruch 4 sich sowohl am Gegenkolben als auch am Pumpengehäuse abstützende Federelement bewirkt eine immer kraftschlüssige, auch beim Saughub des Pumpenkolbens wirksame Abstützung des Gegenkolbens am Abstützlager und kompensiert mit seiner Vorspannkraft F2 eine entsprechende mittlere Vorspannkraft F, der Stösselfeder der Einspritzpumpe. Damit werden auch zusätzlich vom Antrieb herrührende, das Pumpengehäuse beaufschlagende, allerdings im Vergleich zu den Pumpdrücken geringe Antriebskräfte weitgehend von der Einspritzdüse ferngehalten und ebenfalls über den Gegenkolben auf das Abstützlager übertragen. Durch die in Anspruch 5 angegebene Verstellbarkeit des Abstützlagers können Fertigungstoleranzen ausgeglichen und die Vorspannkraft F2 sowie der Totraum bzw. das Volumen des Pumpenarbeitsraumes eingestellt werden.Further advantageous measures and constructive refinements and improvements can be found in subclaims 3 to 6. Thus, by the characterizing features of claim 3, the leakage fuel, which is inevitable even with narrow tolerances, is discharged specifically into a leakage fuel line. The spring element, which is supported both on the counter-piston and on the pump housing, always provides non-positive support of the counter-piston on the support bearing, which is also effective during the suction stroke of the pump piston, and compensates with its preload force F 2 a corresponding mean preload force F, the plunger spring of the injection pump. In this way, additional drive forces originating from the drive, which act on the pump housing, but are low in comparison to the pump pressures, are largely kept away from the injection nozzle and are likewise transmitted to the support bearing via the counter-piston. Due to the adjustability of the support bearing specified in claim 5, manufacturing tolerances can be compensated and the preload force F 2 and the dead space or the volume of the pump work space can be set.

Zeichnungdrawing

Zwei Ausführungsbeispiele der erfindungsgemässen Pumpedüse sind in der Zeichnung dargestellt und werden nachfolgend näher beschrieben. Es zeigen Figur 1 das erste Ausführungsbeispiel anhand einer teilweise im Längsschnitt und stark vereinfacht dargestellten, in den Zylinderkopf der Brennkraftmaschine eingebauten Pumpedüse und Figur 2 einen Längsschnitt durch das zweite, praktisch ausgeführte Ausführungsbeispiel.Two exemplary embodiments of the pump nozzle according to the invention are shown in the drawing and are described in more detail below. FIG. 1 shows the first exemplary embodiment on the basis of a pump nozzle, which is partly shown in longitudinal section and is shown in a highly simplified manner and is built into the cylinder head of the internal combustion engine, and FIG.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In dem in Figur 1 stark vereinfacht dargestellten ersten Ausführungsbeispiel der erfindungsgemässen Pumpedüse 10 nimmt das mit 11 bezeichnete Pumpengehäuse eine Kolbeneinspritzpumpe 12 auf und trägt zusätzlich eine im rechten Winkel zur Längsachse A eines Pumpenkolbens 13 angeord-In the first exemplary embodiment of the pump nozzle 10 according to the invention, which is shown in a highly simplified form in FIG. 1, the pump housing designated 11 receives a piston injection pump 12 and additionally carries a pump pump 13 arranged at right angles to the longitudinal axis A

nete Einspritzdüse 14 bekannter Bauart. Die Einspritzdüse 14 ist über einen seitlich aus einem Pumpenarbeitsraum 15 ausmündenden Druckkanal 16 an diesen Pumpenarbeitsraum 15 angeschlossen und mit einem seitlich, mindestens annähernd rechtwinklig zur Längsachse A des Pumpenkolbens 13 vorspringenden Gehäuseansatz 11 a des Pumpengehäuses 11 verschraubt.Nete injector 14 of a known type. The injection nozzle 14 is connected to this pump work space 15 via a pressure channel 16 opening out laterally from a pump work space 15 and screwed to a housing projection 11 a of the pump housing 11 projecting laterally, at least approximately at right angles to the longitudinal axis A of the pump piston 13.

Die Einspritzdüse 14 ist in eine Aufnahmebohrung 17 eines Zylinderkopfes 18 der zugehörigen Brennkraftmaschine eingesetzt und in an sich bekannter Weise über Spannpratzen oder Stehbolzen 19 am Zylinderkopf 18 befestigt. Durch diese Befestigung wird die gesamte Pumpedüse 10 im Zylinderkopf 18 gehalten, da sich durch die nachstehend im einzelnen beschriebene erfindungsgemässe Ausgestaltung der Pumpedüse 10 eine zusätzliche Befestigung des Einspritzpumpenteiles erübrigt.The injection nozzle 14 is inserted into a receiving bore 17 of a cylinder head 18 of the associated internal combustion engine and is fastened to the cylinder head 18 in a manner known per se via clamping claws or stud bolts 19. By means of this fastening, the entire pump nozzle 10 is held in the cylinder head 18, since an additional fastening of the injection pump part is unnecessary due to the inventive design of the pump nozzle 10 described in detail below.

Der in einem Pumpenzylinder 21 gleitbar geführte Pumpenkolben 13 wird von einem Nocken 22a einer Motornockenwelle 22 der Brennkraftmaschine unter Zwischenschaltung eines Stössels 23 in Hubrichtung, d.h. in Richtung seiner Längsachse A, betätigt und beaufschlagt dabei den Pumpenarbeitsraum 15. Dieser von einem Abschnitt des Pumpenzylinders 21 gebildete Pumpenarbeitsraum 15 ist einerseits vom Pumpenkolben 13 und andererseits von einer inneren Stirnfläche 24a eines Gegenkolbens 24 durch entsprechend enge Passung der zugehörigen Bauteile druckdicht abgeschlossen. Eine der inneren Stirnfläche 24a abgewandte, nach aussen weisende Stirnfläche 24b des Gegenkolbens 24 liegt unter der hydraulischen Kraft des unter Druck im Pumpenarbeitsraum 15 befindlichen Kraftstoffes an einem Abstützlager 25 an und wird deshalb nachfolgend auch als Abstützfläche 24b bezeichnet. Dieses Abstützlager 25 ist ein fester Bestandteil des Zylinderkopfes 18 und nimmt die gesamte, vom Pumpenkolbenantrieb herrührende und über den unter Druck gesetzten Kraftstoff im Pumpenarbeitsraum 15 auf den Gegenkolben 24 übertragene Pump- bzw. Reaktionskraft F auf, so dass das Pumpengehäuse 11 weitgehend entlastet ist. Der als schwimmender Kolben ausgebildete Gegenkolben 24 ist dazu im Bereich eines der Motornokkenwelle 22 abgewandten Endabschnittes 11 b des Pumpengehäuses 11 in eine mit gleichbleibendem Durchmesser D bis zu diesem Endabschnitt 11 b durchgeführte Verlängerung 21 a des Pumpenzylinders 21 eingepasst. Die Abstützfläche 24b des Gegenkolbens 24 bildet dabei die äusserste axiale Erstreckung der Einspritzpumpe 12 in Richtung der Pumpenkolbenlängsachse A.The pump piston 13 slidably guided in a pump cylinder 21 is driven by a cam 22a of an engine camshaft 22 of the internal combustion engine with the interposition of a tappet 23 in the stroke direction, i.e. in the direction of its longitudinal axis A, actuates and acts on the pump work space 15. This pump work space 15, which is formed by a section of the pump cylinder 21, is sealed pressure-tight on the one hand by the pump piston 13 and on the other hand by an inner end face 24a of a counter-piston 24 by means of a correspondingly close fit of the associated components. An outward-facing end face 24b of the counter-piston 24 facing away from the inner end face 24a bears against a support bearing 25 under the hydraulic force of the fuel under pressure in the pump work chamber 15 and is therefore also referred to below as a support surface 24b. This support bearing 25 is an integral part of the cylinder head 18 and absorbs the entire pumping or reaction force F, which originates from the pump piston drive and is transferred to the counter piston 24 via the pressurized fuel in the pump working chamber 15, so that the pump housing 11 is largely relieved. The counter-piston 24, which is designed as a floating piston, is fitted in the region of an end section 11b of the pump housing 11 facing away from the motor camshaft 22 into an extension 21a of the pump cylinder 21 which has a constant diameter D up to this end section 11b. The support surface 24b of the counter-piston 24 forms the outermost axial extension of the injection pump 12 in the direction of the longitudinal axis A of the pump piston A.

Die von den Antriebskräften des Pumpenkolbens 13 auf den im Pumpenarbeitsraum 15 befindlichen Kraftstoff übertragenen Druckkräfte ergeben ihrerseits wiederum die in zwei Richtungen wirkenden und mit F bezeichneten Reaktionskräfte bzw. Pumpkräfte. Da sich die radial wirkenden Kräfte aufheben, ist das Pumpengehäuse 11 durch die Verwendung des Gegenkolbens 24 so weitgehend von in Richtung der Längsachse A des Pumpenkolbens 13 wirkenden Kräften entlastet, dass zu dem bereits bekannten Vorteil der durch die Winkel bauart der Pumpedüse 10 bewirkten niedrigen Bauhöhe die toleranzunempfindliche und von den Pumpkräften entlastete Befestigung der Einspritzdüse 14 im Zylinderkopf 18 als besonders hervorstehender Vorteil der erfindungsgemässen Anordnung zum Tragen kommt.The pressure forces transmitted by the driving forces of the pump piston 13 to the fuel located in the pump working chamber 15 in turn result in the reaction forces or pump forces acting in two directions and designated by F. Since the radially acting forces cancel each other, the use of the counter-piston 24 relieves the pump housing 11 of forces acting in the direction of the longitudinal axis A of the pump piston 13 to such an extent that to the already known advantage of the low overall height caused by the angular design of the pump nozzle 10 the tolerance-insensitive fastening of the injection nozzle 14 in the cylinder head 18, which is relieved of the pump forces, comes into play as a particularly prominent advantage of the arrangement according to the invention.

Bei dem in Figur 2 im Längsschnitt mit allen konstruktiven Einzelheiten dargestellten, praktisch ausgeführten zweiten Ausführungsbeispiel sind im wesentlichen gleiche Bauteile gleich bezeichnet, abweichend gestaltete Teile mit einem Indexstrich versehen und neue Teile neu bezeichnet.In the second embodiment shown in FIG. 2 in longitudinal section with all constructive details, essentially the same components are identified in the same way, parts with a different design are provided with an index line and new parts are given new names.

In die Mantelfläche des ohne einen Bund aus einem vollzylindrischen Teil gleichen Durchmessers gefertigten Gegenkolbens 24'sind, von Pumpenarbeitsraum 15 aus gesehen, drei hintereinander liegende Ringnuten 26, 27 und 28 eingearbeitet, von denen die dem Pumpenarbeitsraum 15 nächstliegende als eine mit einer Leckkraftstoffleitung 29 verbundene Leckkraftstoffrückführnut 26 dient. Die zweite Ringnut 27 nimmt einen den Austritt von Leckkraftstoff nach aussen verhindernden Dichtring 31 auf und in die dritte Ringnut 28 ist ein einen radialen Vorsprung bildender Sprengring 32 eingesetzt. Die von der nach aussen weisenden Stirnfläche gebildete Abstützfläche 24b' am Gegenkolben 24' wird unter der Vorspannkraft eines beim vorliegenden Beispiel von einer Tellerfeder gebildeten Federelements 33 gegen das Abstützlager 25' gedrückt und stützt sich dabei einerseits an dem vom Sprengring 32 gebildeten radialen Vorsprung des Gegenkolbens 24' und andererseits am Endabschnitt 11 b des Pumpengehäuses 11 ab.In the outer surface of the counter-piston 24 ', which is manufactured from a fully cylindrical part of the same diameter without a collar, three annular grooves 26, 27 and 28, one behind the other, are incorporated from the pump work chamber 15, of which the one closest to the pump work chamber 15 is connected as one with a leak fuel line 29 Leak fuel return groove 26 is used. The second annular groove 27 receives a sealing ring 31 which prevents leakage of fuel from escaping to the outside, and a snap ring 32 which forms a radial projection is inserted into the third annular groove 28. The support surface 24b 'on the counter-piston 24' formed by the outward-facing end surface is pressed against the support bearing 25 'under the pretensioning force of a spring element 33 formed in the present example by a plate spring and is supported on the one hand on the radial projection of the counter-piston formed by the snap ring 32 24 'and on the other hand from the end section 11b of the pump housing 11.

Das Abstützlager 25' für den Gegenkolben 24' ist von einem zur Einstellung seiner Einbaulage verstellbaren, in den Zylinderkopf 18 der Brennkraftmaschine eingeschraubten und lagegesichert befestigten Schraubteil gebildet. Dadurch können Einbautoleranzen ausgeglichen werden. Der Einbau der Pumpedüse 10' wird zudem bei nach rechts herausgedrehtem Abstützlager 25' erleichtert und die Einbaulage des Gegenkolbens 24' kann stufenlos eingestellt werden. Dabei können einerseits Fertigungstoleranzen ausgeglichen werden und andererseits die Vorspannkraft F2 der Tellerfeder 33 so verändert werden, dass sie gleich der mit F1 bezeichneten Kraft gemacht werden kann. Bei F1 handelt es sich um den Mittelwert der bei den Hubbewegungen des Pumpenkolbens 13 vom Stössel 23 auf eine Stösselfeder 34 und von dieser über einen Flansch 35a einer Führungshülse 35 für den Stössel 23 auf das Pumpengehäuse 11 übertragenen Vorspannkraft ist. Die die Kräfte F1 und F2 darstellenden Pfeile sind der klareren Darstellung wegen nach aussen versetzt eingezeichnet worden. Die rein bauraummässigen Vorteile der gewählten Bauart der Pumpedüse 10' ist aus Figur 2 besonders deutlich zu ersehen.The support bearing 25 'for the counter-piston 24' is formed by a screw part which is adjustable to adjust its installation position, is screwed into the cylinder head 18 of the internal combustion engine and is secured in position. This allows installation tolerances to be compensated for. The installation of the pump nozzle 10 'is also facilitated when the support bearing 25' is screwed out to the right, and the installation position of the counter-piston 24 'can be adjusted continuously. On the one hand, manufacturing tolerances can be compensated for and, on the other hand, the pretensioning force F 2 of the plate spring 33 can be changed so that it can be made equal to the force denoted by F 1 . F 1 is the mean value of the pretensioning force transmitted from the plunger 23 to a plunger spring 34 during the lifting movements of the pump piston 13 and from this via a flange 35a of a guide sleeve 35 for the plunger 23 to the pump housing 11. The arrows representing the forces F 1 and F 2 have been drawn in outwards for clarity. The purely space-related advantages of the selected design of the pump nozzle 10 'can be seen particularly clearly from FIG.

Claims (7)

1. Pump injector for fuel injection in internal combustion engines, particularly for diesel engines, comprising a pump casing (11)whichholds a piston injection pump (12) and carries an injection nozzle (14) and which holds a pump piston (13) adapted to be actuated by means of a tappet (23) of an engine camshaft (22) and to slide in a pump cylinder (21) and also contains a pump working chamber (15) which is loadable by the pump piston (13) and to which the injection nozzle (14) is connected via a pressure duct (16) which leads out laterally;
also comprising a casing attachment (1 a) which projects laterally and at least approximately at right angles to the longitudinal axis (A) of the pump piston (13) and to which the injection nozzle (14) inserted into a receiving bore (17) on the cylinder head (18) of the internal combustion engine is screwed; and
further comprising a support surface (24b) which forms the outermost boundary of the axial length of the injection pump (12) and is situated in the region of an end portion (11 b), remote from the engine camshaft (22), of the pump casing (11), and which lies against a support bearing (25) on the cylinder head (18) of the internal combustion engine,

characterized in that the supporting surface (24b; 24b') lying against the support bearing (25, 25') is formed by an outwardly facing end face of an opposed piston (24; 24') which is inserted into the pump cylinder (21 ) in line with the longitudinal axis (A) of the pump piston and pressuretightly closes the pump working chamber (15) by means of an inner end face (24a).
2. Pump injector according to Claim 1, characterized in that the opposed piston (24; 24') is fitted, as a floating piston, into an extension (21 a) of the pump cylinder (21), which extension extends with uniform diameter (D) to the end portion (11 b) of the pump casing (11).
3. Pump injector according to Claim 2, characterized in that in the peripheral surface of the opposed piston (24') there are provided at least two annular grooves (26, 27), of which the one lying nearest the pump working chamber (15) serves as a fuel leak return groove (26) connected to a fuel leak pipe (29) and the second annular groove (27) holds a sealing ring (31 ).
4. Pump injector according to Claim 2 or 3, characterized in that the supporting surface (24b') of the opposed piston (24') is pressed against the support bearing (25') by the prestress force of a spring element (33) supported against the end portion ( 11 b) of the pump casing (11) and a radial projection (32) on the opposed piston (24').
5. Pump injector according to one of Claims 1 to 4, characterized in that the support bearing (25') for the opposed piston (24') is formed by an adjustable screw part screwed into the cylinder head (18) of the internal combustion engine and secured in position.
6. Pump injector according to Claim 4 in conjunction with Claim 3, characterized in that the radial projection (32) on the opposed piston (24') is formed by a circlip inserted into a third annular groove (28).
EP84902788A 1983-07-29 1984-07-17 Pump injector for fuel injection of internal combustion engines Expired EP0153331B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84902788T ATE23209T1 (en) 1983-07-29 1984-07-17 PUMP NOZZLE FOR FUEL INJECTION IN COMBUSTION ENGINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3327399 1983-07-29
DE19833327399 DE3327399A1 (en) 1983-07-29 1983-07-29 PUMPEDUESE FOR FUEL INJECTION IN INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0153331A1 EP0153331A1 (en) 1985-09-04
EP0153331B1 true EP0153331B1 (en) 1986-10-29

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ID=6205243

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Application Number Title Priority Date Filing Date
EP84902788A Expired EP0153331B1 (en) 1983-07-29 1984-07-17 Pump injector for fuel injection of internal combustion engines

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US (1) US4615323A (en)
EP (1) EP0153331B1 (en)
JP (1) JPS60501909A (en)
DE (2) DE3327399A1 (en)
WO (1) WO1985000638A1 (en)

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Also Published As

Publication number Publication date
WO1985000638A1 (en) 1985-02-14
US4615323A (en) 1986-10-07
JPH0444104B2 (en) 1992-07-20
EP0153331A1 (en) 1985-09-04
DE3461113D1 (en) 1986-12-04
DE3327399A1 (en) 1985-02-21
JPS60501909A (en) 1985-11-07

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