EP0261154B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0261154B1
EP0261154B1 EP87901395A EP87901395A EP0261154B1 EP 0261154 B1 EP0261154 B1 EP 0261154B1 EP 87901395 A EP87901395 A EP 87901395A EP 87901395 A EP87901395 A EP 87901395A EP 0261154 B1 EP0261154 B1 EP 0261154B1
Authority
EP
European Patent Office
Prior art keywords
shaft
pump
shaft part
fuel injection
injection pump
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
EP87901395A
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German (de)
French (fr)
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EP0261154A1 (en
Inventor
Walter Häfele
Manfred KRÄMER
Johann Warga
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0261154A1 publication Critical patent/EP0261154A1/en
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    • 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of the main claim.
  • the exact and also synchronous control of the control slide is important for the injection quality and thus the combustion quality in the engine.
  • Higher loads on the torsion shaft such as occur during jerky twisting, can lead to a slight bending of the torsion shaft, which not only falsifies the synchronization of the individual control slides to one another, but also considerable additional friction can occur at the bearing points of the torsion shaft. Since the shaft is rotated by a controller, the adjustment forces of which are sensitive and dependent on the speed, variable frictional forces in particular have a negative effect on the control quality.
  • the fuel injection pump according to the invention with the characterizing features of the claim has the advantage that no bending stresses are transmitted to the bearings due to the cardanic rotational connection between the two shaft parts.
  • the bearing of the second shaft part on the drive side of the torsion shaft can work stress-free and therefore almost frictionless. Due to this lateral force relief, the bearing between the second shaft part and the pump housing can be designed in a very fine fit, as is common, for example, between the injection pump piston and the cylinder, so that there is extensive tightness against fuel outflow from the injection pump into the regulator.
  • the one shaft part on the coupling side has a slightly convex end pin which runs in the shaft axis and is mounted in a corresponding blind hole on the end side of the other shaft part.
  • the shaft parts each have an expanded section on the mutually facing end faces, for example a collar on which driving claws or recesses are provided for the rotational connection.
  • a collar on which driving claws or recesses are provided for the rotational connection e.g. a large collar, on which an axial nose is attached, which engages in a corresponding recess of the opposite collar, creates a favorable lever arm for taking along without adverse transverse forces.
  • the second shaft part is mounted in a central bore of a bearing bush, which is arranged in a pump housing bore by means of sealing rings and in which an oil ring groove with an relief channel leading to the outside is present in the central bore, advantageously the second shaft part is guided in this central bore in the manner of an injection pump element seal. Since there is hardly any axial movement of the second shaft part, little fuel will leak through between the shaft and the bore if the fit is good. These small quantities are then caught and drained through the oil ring groove, so that no diesel fuel from the injection pump gets into the regulator, in which it could inadmissibly dilute the lubricating oil present there (leakage fuel return).
  • a shaft end runs at the free end of the first shaft part in a blind bore of a bearing cover inserted in a bore of the pump housing, a pin located at the shaft end also being spherical here.
  • the spherical design enables tension-free turning of the adjustment shaft.
  • annular groove is present in the shaft end dipping into the blind bore, into which a locking pin arranged in the bearing cover or housing engages as a safeguard against axial displacement of the first shaft part.
  • EP-A-0 0150 343 describes a fuel injection pump in which the control rod mounted at both ends in the housing is divided between the bearings (see FIGS. 3, 4, 6 and 7).
  • a longitudinally displaceable control rod is divided into a first control rod part, which has free ends in the pump housing and a second control rod part, which, however, is non-positively, i.e. firmly coupled to the first control rod part and sealed in the pump housing, and one is sealed forms radial guidance for the end of the first control rod part facing it.
  • the guide collars provided for guiding the second control rod part are very short, that is to say they are narrower than their diameter, so that only "quasi-cardanic" mounting can be achieved. Since, due to this short guide length, the corresponding sealing gap is also relatively short, a relatively good seal, which is not suitable for all applications and especially not suitable for a rotary shaft, can be achieved with such a construction.
  • FIG. 1 shows a longitudinal section through a fuel injection pump according to the invention along line I-I in FIG. 2; 2 shows a cross section through this pump along line 11-11 in FIG. 1, only one pump piston and control slide being shown in cross section, and FIGS. 3 and 4 end shields of the adjusting shaft according to section 111-111 in FIG. 2 and according to view IV in Fig. 2.
  • cylinder liners 2 are embedded in series in a housing 1, in each of which a pump piston 3, with the interposition of a roller tappet 4 with roller 5, is driven by a camshaft 6 against the force of a spring 7 for its axial movement forming the working stroke.
  • Partial suction chambers 8 are formed by cutouts in the cylinder liners 2, each of which is assigned to a pump element formed from the cylinder liner 2 and the pump piston 3.
  • a control slide 9 is arranged axially displaceably on the pump piston 3.
  • the individual partial suction chambers 8 open on the outlet side into a main suction chamber 10 which extends over the length of the housing 1 and is closed at its longitudinal ends by end shields 11.
  • a rotating shaft 12 is arranged, which is rotatably mounted in the end shields 11 and through which the control slide 9 are displaceable.
  • driving pins 14a In transverse bores of the rotating shaft 12 there are radially protruding driving pins 14a, each of which engages in a groove 13 of the control slide 9, namely as end sections of an eccentric bolt 14, which can be fixed in position on the rotating shaft 12 by means of a clamping nut 15.
  • a locking plug 16 of which only two are shown in FIG. 2, is provided in each case opposite these clamping nuts 15, after removal of which an adjustment of the individual driving pins 14a after loosening and tightening the clamping nut 15 is possible, in order in this way the individual control slides 9 to adjust to each other.
  • These oblique grooves 24 interact with radial bores 25 of the control slide 9 in that they are opened by these radial bores 25 after a certain stroke of the pump piston 3 and thus serve as control openings.
  • a guide pin 26 is arranged in the cylinder liner 2, which engages in a longitudinal groove 27 of the control slide 9.
  • the pump piston 3 has at its lower section a flattened area 28 on which a driving member 31, which can be rotated by a control rod 29 in a known manner, engages, so that an axial displacement of the control rod 29, a rotation of the pump piston 3 and thus a change in the assignment of the oblique grooves 24 to the radial bores 25.
  • a suction hole 32 is provided, which is exposed by the pump piston 3 in its bottom dead center position (as shown in the drawing).
  • the fuel supply to the individual partial suction chambers 8 takes place through an inflow channel 33 which runs in a pipe 34 laid in the housing 1.
  • this tube 34 there are radial branch openings 35 which open into openings 36 connected to the partial suction chambers 8.
  • the torsion shaft 12 consists of two shaft parts which are connected to one another in a rotationally locking manner via a claw coupling 37, namely a first shaft part 38 which supports the eccentric bolts 14 and a second shaft part 39 which acts on the regulator from outside the pump.
  • the two shaft parts 38 and 39 are axially inserted into one another, for which purpose a blind hole 40 is provided in the corresponding end face of the first shaft part 38 and there is a slightly curved pin 41 which plunges into this blind hole 40 and which provides a support for this end of the first shaft part 38.
  • the two mutually facing end faces of the shaft parts are widened like a flange, so that two frets 42 lie opposite one another. While a claw 43 is located on one collar, a corresponding recess 44 is provided on the other collar.
  • the second shaft part 39 itself is mounted in a central bore 45 of a bearing bush 46, which is inserted in the housing bore receiving this end shield and is held by a screw 47. Between the housing 1 and this bearing bush 46 are two rings 48 available. An oil ring groove 49 is arranged in the central bore 45, from which a relief channel 51 branches off. This second shaft part 39 is guided in the central bore 45 with very little play, as is the case, for example, when guiding the pump piston in the cylinder. The oil ring groove 49 collects the fuel that may still leak through from the main suction chamber 10 and discharges it via the relief channel 51 in order not to get into the regulator housing filled with lubricating oil (leakage fuel return).
  • a shaft end 54 of the first shaft part 38 is mounted in a blind bore 52 of the second bearing plate 11 designed as a bearing cover 53.
  • the shaft end 54 has a pin 54a, which is also crowned to have only line contact for storage, so that slight bending of the shaft part 38 or an incorrectly aligned installation position of the bearing cover 53 does not lead to any additional frictional forces.
  • the axial position of the first shaft part 38 is secured by a pin 55 which engages in an annular groove 56 of the shaft part 38 and is arranged in the bearing cover 53.
  • a flattening 57 is present on the shaft end 54 between the ring groove 56 and the pin 54a, which reaches approximately the same depth as the ring groove 56. This makes it possible to push this free end of the first shaft part 38 into the blind bore 52 at the location of the flattened portion 57 in order to then turn the shaft part 38 in a bayonet-like manner so that the pin 55 engages in the annular groove 56.
  • the bearing cover 53 is fastened to the housing by screws 58.
  • the rotation shaft 12 is assembled as follows: First, the first part 38 of the rotation shaft is pushed into the pump housing, namely rotated by 90 degrees with respect to the operating position. Then this shaft is rotated back into the working position by 90 degrees and inserted with the driving pins 14a into the grooves 13 of the control slide 9. Then the two end shields are mounted, namely the bearing cover 53 in the manner described by bayonet-like turning, then the bearing bush 46 with the second shaft part 39 already installed.

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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

Fuel injection pump for internal combustion engines with several pump elements (2, 3) arranged in series, in which the initiation of injection is effected by a distributor (9) which can be slid axially on the pump piston (3) and by controlling the discharge ducts (22 to 25) of the pump working chambers (18). The pump distributors (9) are actuated via a torque shaft (12) which is designed in two parts, namely a first shaft part (38) which preferably is secured axially and a second shaft part (39) which is inserted in a leakproof manner in a bearing sleeve arranged in the housing. The two shaft parts are inserted in one another by a spigot (41) and a blind hole (40) arranged on the front ends facing one another and are linked together by a claw coupling (43, 44) so as to lock during rotation.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Hauptanspruchs. Bei derartigen schiebergesteuerten Einspritzpumpen ist für die Einspritzqualität und damit die Verbrennungsqualität im Motor die exakte und auch synchrone Führung der Steuerschieber von Bedeutung. Höhere Belastungen an der Verdrehwelle, wie sie beispielsweise beim ruckartigen Verdrehen auftreten, können zu einem leichten Ausbiegen der Verdrehwelle führen, wodurch nicht nur die Synchronisation der einzelnen Steuerschieber zueinander verfälscht wird, sondern auch an den Lagerstellen der Verdrehwelle erhebliche zusätzliche Reibungen auftreten können. Da die Verdrehung der Welle über einen Regler erfolgt, dessen Verstellkräfte sensibel und drehzahlabhängig sind, wirken sich vor allem veränderliche Reibkräfte nachteilig auf die Regelungsqualität aus.The invention relates to a fuel injection pump for internal combustion engines according to the preamble of the main claim. In such slide-controlled injection pumps, the exact and also synchronous control of the control slide is important for the injection quality and thus the combustion quality in the engine. Higher loads on the torsion shaft, such as occur during jerky twisting, can lead to a slight bending of the torsion shaft, which not only falsifies the synchronization of the individual control slides to one another, but also considerable additional friction can occur at the bearing points of the torsion shaft. Since the shaft is rotated by a controller, the adjustment forces of which are sensitive and dependent on the speed, variable frictional forces in particular have a negative effect on the control quality.

Wie bei fast allen Einspritzpumpen dieser Art, ist auch bei einer gattungsgemäßen Einspritzpumpe (US-A-3667437) die Lagerung der Verdrehwelle auf der Antriebsseite als einfaches Gleitlager ausgebildet, das nur unvollkommen eine Art Ölsperre zum Regler hin bildet, denn außer Dicht- und Reibungsproblemen bestehen auch bei der Fertigung derartiger Lagerungen Fertigungsprobleme, da die Gehäusebohrungen zur Aufnahme der Lagerbuchsen absolut gleichachsig mit der Verdrehwelle verlaufen müssen, um beim Verdrehen Lagerverspannungen zu vermeiden. Solche Vc Spannungen führen entweder zu unvertretbaren zusätzlichen Reibkräften oder zum Ausschlagen und axialen Undichtwerden des Lagers.As with almost all injection pumps of this type, with a generic injection pump (US-A-3667437) the bearing of the torsion shaft on the drive side is designed as a simple plain bearing, which only imperfectly forms an oil lock to the controller, because apart from sealing and friction problems There are also manufacturing problems in the manufacture of such bearings, since the housing bores for receiving the bearing bushes must run absolutely coaxially with the torsion shaft in order to avoid bearing stresses during rotation. Such Vc tensions either lead to unacceptable additional frictional forces or to the knocking out and axial leakage of the bearing.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs hat demgegenüber den Vorteil, daß aufgrund der kardanischen Drehschlüssigkeit zwischen den beiden Wellenteilen keine Biegespannungen auf die Lager übertragen werden. Besonders das Lager des zweiten Wellenteils auf der Antriebsseite der Verdrehwelle kann spannungsfrei und dadurch nahezu reibungsfrei arbeiten. Aufgrund dieser Querkraftentlastung kann das Lager zwischen zweitem Wellenteil und Pumpengehäuse in sehr feiner Passung, wie sie beispielsweise zwischen Einspritzpumpenkolben und Zylinder üblich ist, ausgebildet werden, so daß eine weitgehende Dichtheit gegen Ausströmen von Kraftstoff aus der Einspritzpumpe in den Regler gegeben ist. Dazu weist als radiale Führung der eine Wellenteil auf der Kopplungsseite einen in Wellenachse verlaufenden, leicht balligen Stirnzapfen auf, der in einer entsprechenden Sackbohrung auf der Stirnseite des anderen Wellenteils gelagert ist. Durch diese Art der Führung und Lagerung der beiden Wellenteile wird eine verspannungsfreie Lagerung erreicht, ohne daß sich leichte Fluchtungsfehler der Längsachsen der beiden Wellenteile in Form von Verspannungen nachteilig auswirken.The fuel injection pump according to the invention with the characterizing features of the claim has the advantage that no bending stresses are transmitted to the bearings due to the cardanic rotational connection between the two shaft parts. In particular, the bearing of the second shaft part on the drive side of the torsion shaft can work stress-free and therefore almost frictionless. Due to this lateral force relief, the bearing between the second shaft part and the pump housing can be designed in a very fine fit, as is common, for example, between the injection pump piston and the cylinder, so that there is extensive tightness against fuel outflow from the injection pump into the regulator. For this purpose, as a radial guide, the one shaft part on the coupling side has a slightly convex end pin which runs in the shaft axis and is mounted in a corresponding blind hole on the end side of the other shaft part. This type of guidance and mounting of the two shaft parts achieves tension-free mounting without slight misalignment of the longitudinal axes of the two shaft parts in the form of tension having a disadvantageous effect.

Nach einer vorteilhaften Ausgestaltung der Erfindung weisen die Wellenteile an den einander zugewandten Stirnseiten je einen erweiterten Abschnitt auf, beispielsweise einen Bund, an dem Mitnahmeklauen oder -ausnehmungen für den Drehschluß vorhanden sind. Durch diesen erweiterten Abschnitt, z.B. einen großen Bund, an dem eine Axialnase angebracht ist, die in eine entsprechende Ausnehmung des gegenüberliegenden Bundes greift, entsteht ein günstiger Hebelarm für die Mitnahme ohne nachteilige Querkräfte.According to an advantageous embodiment of the invention, the shaft parts each have an expanded section on the mutually facing end faces, for example a collar on which driving claws or recesses are provided for the rotational connection. Through this expanded section, e.g. a large collar, on which an axial nose is attached, which engages in a corresponding recess of the opposite collar, creates a favorable lever arm for taking along without adverse transverse forces.

Nach einer wichtigen Ausgestaltung der Erfindung ist der zweite Wellenteil in einer zentralen Bohrung einer Lagerbuchse gelagert, der in einer Pumpengehäusebohrung durch Dichtringe radial dichtend angeordnet ist und wobei in der zentralen Bohrung eine Ölringnut mit einem nach außen führenden Entlastungskanal vorhanden ist, wobei vorteilhafterweise der zweite Wellenteil in dieser zentralen Bohrung in Art einer Einspritzpumpenelementdichtung geführt ist. Da kaum axiale Bewegungen des zweiten Wellenteils vorhanden sind, wird bei einer guten Passung auch wenig Kraftstoff zwischen Welle und Bohrung durchlecken. Diese geringen Mengen werden dann aber durch die Ölringnut aufgefangen und abgeleitet, so daß kein Dieselkraftstoff aus der Einspritzpumpe in den Regler gelangt, in dem er das dort vorhandene Schmieröl unzulässig verdünnen könnte (Leckkraftstoffrückführung).According to an important embodiment of the invention, the second shaft part is mounted in a central bore of a bearing bush, which is arranged in a pump housing bore by means of sealing rings and in which an oil ring groove with an relief channel leading to the outside is present in the central bore, advantageously the second shaft part is guided in this central bore in the manner of an injection pump element seal. Since there is hardly any axial movement of the second shaft part, little fuel will leak through between the shaft and the bore if the fit is good. These small quantities are then caught and drained through the oil ring groove, so that no diesel fuel from the injection pump gets into the regulator, in which it could inadmissibly dilute the lubricating oil present there (leakage fuel return).

Nach einer weiteren Ausgestaltung der Erfindung läuft ein Wellenende am freien Ende des ersten Wellenteils in einer Sackbohrung eines in einer Bohrung des Pumpengehäuses eingesetzten Lagerdeckels, wobei auch hier ein am Wellenende befindlicher Zapfen ballig ausgebildet ist. Besonders durch die ballige Ausführung ist ein spannungsfreies Verdrehen der Verstellwelle ermöglicht.According to a further embodiment of the invention, a shaft end runs at the free end of the first shaft part in a blind bore of a bearing cover inserted in a bore of the pump housing, a pin located at the shaft end also being spherical here. The spherical design enables tension-free turning of the adjustment shaft.

In ergänzender Ausgestaltung der Erfindung ist in dem in die Sackbohrung tauchenden Wellenende eine Ringnut vorhanden, in die ein im Lagerdeckel oder Gehäuse angeordneter Sicherungsstift als Sicherung gegen axiales Verschieben des ersten Wellenteils greift.In a supplementary embodiment of the invention, an annular groove is present in the shaft end dipping into the blind bore, into which a locking pin arranged in the bearing cover or housing engages as a safeguard against axial displacement of the first shaft part.

Die erste Merkmalsgruppe aus dem Kennzeichenteil des Patentanspruchs 1 ist, allerdings in abgewandelter Form, aus dem Stand der Technik bekannt. So ist in der EP-A-0 0150 343 eine Kraftstoffeinspritzpumpe beschrieben, bei der die im Gehäuse an beiden Enden gelagerte Regelstange zwischen den Lagern geteilt ist (siehe Figuren 3, 4, 6 und 7). Dort ist die, im Gegensatz zur erfindungsgemäßen Drehwelle längsverschiebliche Regelstange unterteilt in einen Mitnehmerschlitze aufweisenden, mit seinem freien Ende im Pumpengehäuse gelagerten ersten Regelstangenteil und einen zweiten Regelstangenteil, der jedoch kraftschlüssig, d.h. fest mit dem ersten Regelstangenteil gekoppelt sowie im Pumpengehäuse dichtend gelagert ist und eine radiale Führung für das ihm zugewandte Ende des ersten Regelstangenteils bildet. Um bei dieser Konstruktion durch Fluchtungsfehler hervorgerufene Verspannungen auszuschalten, sind die zur Führung des zweiten Regelstangenteils vorgesehenen Führungsbunde sehr kurz, d.h. schmaler als ihr Durchmesser ausgebildet, so daß dadurch eine nur "quasi-kardanische" Lagerung erzielt werden kann. Da wegen dieser kurzen Führungslänge auch der entsprechende Dichtspalt relativ kurz ist, ist wohl eine relativ gute, jedoch nicht für alle Anwendungsfälle und vor allem nicht für eine Drehwelle geeignete Abdichtung mit einer solchen Konstruktion erreichbar.The first group of features from the characterizing part of claim 1 is, however in a modified form, known from the prior art. For example, EP-A-0 0150 343 describes a fuel injection pump in which the control rod mounted at both ends in the housing is divided between the bearings (see FIGS. 3, 4, 6 and 7). There, in contrast to the rotary shaft according to the invention, a longitudinally displaceable control rod is divided into a first control rod part, which has free ends in the pump housing and a second control rod part, which, however, is non-positively, i.e. firmly coupled to the first control rod part and sealed in the pump housing, and one is sealed forms radial guidance for the end of the first control rod part facing it. To at this To eliminate tension caused by misalignment, the guide collars provided for guiding the second control rod part are very short, that is to say they are narrower than their diameter, so that only "quasi-cardanic" mounting can be achieved. Since, due to this short guide length, the corresponding sealing gap is also relatively short, a relatively good seal, which is not suitable for all applications and especially not suitable for a rotary shaft, can be achieved with such a construction.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt, und im folgenden näher beschrieben.An embodiment of the object of the invention is shown in the drawing and described in more detail below.

Es zeigen Fig. 1 einen Längsschnitt durch eine erfindungsgemäße Kraftstoffeinspritzpumpe nach Linie I-I in Fig. 2; Fig. 2 einen Querschnitt durch diese Pumpe nach Linie 11-11 in Fig. 1, wobei nur ein Pumpenkolben und Steuerschieber im Querschnitt dargestellt ist und Fig. 3 und 4 Lagerschilde der Verstellwelle nach Schnitt 111-111 in Fig. 2 und nach Ansicht IV in Fig. 2.1 shows a longitudinal section through a fuel injection pump according to the invention along line I-I in FIG. 2; 2 shows a cross section through this pump along line 11-11 in FIG. 1, only one pump piston and control slide being shown in cross section, and FIGS. 3 and 4 end shields of the adjusting shaft according to section 111-111 in FIG. 2 and according to view IV in Fig. 2.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei der dargestellten Kraftstoffeinspritzpumpe sind in einem Gehäuse 1 sechs Zylinderbüchsen 2 in Reihe eingelassen, in denen jeweils ein Pumpenkolben 3 unter Zwischenschaltung eines Rollenstößels 4 mit Rolle 5 durch eine Nockenwelle 6 entgegen der Kraft einer Feder 7 für seine den Arbeitshub bildende axiale Bewegung angetrieben wird. Durch Aussparungen in den Zylinderbüchsen 2 werden Teilsaugräume 8 gebildet, die jeweils einem aus Zylinderbüchse 2 und Pumpenkolben 3 gebildeten Pumpenelement zugeordnet sind. In diesen Teilsaugräumen 8 ist auf den Pumpenkolben 3 axial verschiebbar je ein Steuerschieber 9 angeordnet.In the fuel injection pump shown, six cylinder liners 2 are embedded in series in a housing 1, in each of which a pump piston 3, with the interposition of a roller tappet 4 with roller 5, is driven by a camshaft 6 against the force of a spring 7 for its axial movement forming the working stroke. Partial suction chambers 8 are formed by cutouts in the cylinder liners 2, each of which is assigned to a pump element formed from the cylinder liner 2 and the pump piston 3. In these partial suction chambers 8, a control slide 9 is arranged axially displaceably on the pump piston 3.

Die einzelnen Teilsaugräume 8 münden abflußseitig in einen sich über die Länge des Gehäuses 1 erstreckenden Hauptsaugraum 10, der an seinen Längsenden durch Lagerschilde 11 verschlossen ist. In diesem Hauptsaugraum 10 ist eine Verdrehwelle 12 angeordnet, die in den Lagerschilden 11 verdrehbar gelagert ist und durch die die Steuerschieber 9 verschiebbar sind. In Querbohrungen der Verdrehwelle 12 sind radial herausragende und in je eine Nut 13 der Steuerschieber 9 greifende Mitnahmezapfen 14a vorhanden und zwar als Endabschnitte je eines Exzenterbolzens 14 gebildet, der mittels einer Spannmutter 15 in seiner Lage an der Verdrehwelle 12 fixierbar ist. Im Gehäuse 1 ist jeweils gegenüber diesen Spannmuttern 15 ein Verschlußstopfen 16, von denen nur zwei in Fig. 2 dargestellt sind, vorgesehen, nach dessen Entfernen eine Justierung der einzelnen Mitnahmezapfen 14a nach Lockern und Wiederfestspannen der Spannmutter 15 möglich wird, um so die einzelnen Steuerschieber 9 zueinander zu justieren.The individual partial suction chambers 8 open on the outlet side into a main suction chamber 10 which extends over the length of the housing 1 and is closed at its longitudinal ends by end shields 11. In this main suction chamber 10, a rotating shaft 12 is arranged, which is rotatably mounted in the end shields 11 and through which the control slide 9 are displaceable. In transverse bores of the rotating shaft 12 there are radially protruding driving pins 14a, each of which engages in a groove 13 of the control slide 9, namely as end sections of an eccentric bolt 14, which can be fixed in position on the rotating shaft 12 by means of a clamping nut 15. In the housing 1, a locking plug 16, of which only two are shown in FIG. 2, is provided in each case opposite these clamping nuts 15, after removal of which an adjustment of the individual driving pins 14a after loosening and tightening the clamping nut 15 is possible, in order in this way the individual control slides 9 to adjust to each other.

Der Pumpenkolben 3, die Zylinderbüchse 2 und ein Druckventil 17 begrenzen einen Pumpenarbeitsraum 18, von dem ein Druckkanal 19 zu einer vereinfacht dargestellten Druckleitung 20 führt, die an einer Einspritzdüse 21 der Brennkraftmaschine endet. Im Pumpenkolben 3 ist eine in den Pumpenarbeitsraum 18 mündende Sackbohrung 22 vorhanden sowie eine Querbohrung 23, die in Schrägnuten 24 mündet, die auf einander abgewandten Seiten in die Mantelfläche des Pumpenkolbens 3 eingearbeitet sind. Diese Schrägnuten 24 wirken mit Radialbohrungen 25 des Steuerschiebers 9 zusammen, indem sie nach Zurücklegung eines bestimmten Hubes des Pumpenkolbens 3 durch diese Radialbohrungen 25 aufgesteuert werden und so als Steueröffnungen dienen.The pump piston 3, the cylinder liner 2 and a pressure valve 17 delimit a pump working chamber 18, from which a pressure channel 19 leads to a simplified pressure line 20, which ends at an injection nozzle 21 of the internal combustion engine. In the pump piston 3 there is a blind bore 22 opening into the pump working chamber 18 and a transverse bore 23 which opens into oblique grooves 24 which are incorporated into the lateral surface of the pump piston 3 on sides facing away from one another. These oblique grooves 24 interact with radial bores 25 of the control slide 9 in that they are opened by these radial bores 25 after a certain stroke of the pump piston 3 and thus serve as control openings.

Damit der Steuerschieber 9 bei seiner axialen Verschiebung auf dem Pumpenkolben 3 gegen Verdrehen gesichert ist und damit eine exakte Zuordnung von Schrägnuten 24 und Radialbohrungen 25 gewährleistet ist, ist in der Zylinderbüchse 2 ein Führungsstift 26 angeordnet, der in eine Längsnut 27 des Steuerschiebers 9 greift. Der Pumpenkolben 3 weist an seinem unteren Abschnitt eine Abflachung 28 auf, an der ein durch eine Regelstange 29 in bekannter Weise verdrehbares Mitnahmeglied 31 angreift, so daß ein axiales Verschieben der Regelstange 29, ein Verdrehen des Pumpenkolbens 3 und damit ein Ändern der Zuordnung der Schrägnuten 24 zu den Radialbohrungen 25 bewirkt.So that the control slide 9 is secured against rotation during its axial displacement on the pump piston 3 and thus an exact assignment of oblique grooves 24 and radial bores 25 is ensured, a guide pin 26 is arranged in the cylinder liner 2, which engages in a longitudinal groove 27 of the control slide 9. The pump piston 3 has at its lower section a flattened area 28 on which a driving member 31, which can be rotated by a control rod 29 in a known manner, engages, so that an axial displacement of the control rod 29, a rotation of the pump piston 3 and thus a change in the assignment of the oblique grooves 24 to the radial bores 25.

In der Zylinderbüchse 2 ist eine Saugbohrung 32 vorgesehen, die vom Pumpenkolben 3 in dessen unterer Totpunktlage (wie in der Zeichnung dargestellt) freigelegt wird.In the cylinder liner 2, a suction hole 32 is provided, which is exposed by the pump piston 3 in its bottom dead center position (as shown in the drawing).

Die Kraftstoffversorgung der einzelnen Teilsaugräume 8 erfolgt durch einen Zuströmkanal 33, der in einem im Gehäuse 1 verlegten Rohr 34 verläuft. In diesem Rohr 34 sind radiale Abzweigöffnungen 35 vorhanden, die in mit den Teilsaugräumen 8 verbundenen Öffnungen 36 münden.The fuel supply to the individual partial suction chambers 8 takes place through an inflow channel 33 which runs in a pipe 34 laid in the housing 1. In this tube 34 there are radial branch openings 35 which open into openings 36 connected to the partial suction chambers 8.

Die Verdrehwelle 12 besteht aus zwei über eine Klauenkupplung 37 drehschlüssig miteinander verbundenen Wellenteilen nämlich einem ersten die Exzenterbolzen 14 tragenden Wellenteil 38 und einem zweiten von außerhalb der Pumpe nämlich dem Regler her angreifenden zweiten Wellenteil 39. Die beiden Wellenteile 38 und 39 sind axial ineinandergesteckt, wofür eine Sackbohrung 40 in der entsprechenden Stirnseite des ersten Wellenteils 38 vorgesehen ist und ein in diese Sackbohrung 40 tauchender leicht gewölbter Zapfen 41 vorhanden ist, der diesem Ende des ersten Wellenteils 38 ein Auflager bietet. Im übrigen sind die beiden einander zugewandten Stirnseiten der Wellenteile flanschartig erweitert, so daß sich zwei Bünde 42 gegenüberliegen. Während sich an dem einen Bund eine Klaue 43 befindet, ist an dem anderen Bund eine entsprechende Ausnehmung 44 vorhanden.The torsion shaft 12 consists of two shaft parts which are connected to one another in a rotationally locking manner via a claw coupling 37, namely a first shaft part 38 which supports the eccentric bolts 14 and a second shaft part 39 which acts on the regulator from outside the pump. The two shaft parts 38 and 39 are axially inserted into one another, for which purpose a blind hole 40 is provided in the corresponding end face of the first shaft part 38 and there is a slightly curved pin 41 which plunges into this blind hole 40 and which provides a support for this end of the first shaft part 38. Otherwise, the two mutually facing end faces of the shaft parts are widened like a flange, so that two frets 42 lie opposite one another. While a claw 43 is located on one collar, a corresponding recess 44 is provided on the other collar.

Der zweite Wellenteil 39 selbst ist in einer zentralen Bohrung 45 einer Lagerbuchse 46 gelagert, die in der diesen Lagerschild aufnehmenden Gehäusebohrung eingesetzt und durch eine Schraube 47 gehalten wird. Zwischen Gehäuse 1 und dieser Lagerbuchse 46 sind zwei Ringdichtungen 48 vorhanden. In der zentralen Bohrung 45 ist eine Ölringnut 49 angeordnet, von der ein Entlastungskanal 51 abzweigt. Dieser zweite Wellenteil 39 ist in der zentralen Bohrung 45 mit sehr geringem Spiel, wie es beispielsweise bei der Führung vom Pumpenkolben im Zylinder gegeben ist, geführt. Durch die Ölringnut 49 wird der möglicherweise trotzdem vom Hauptsaugraum 10 her durchleckende Kraftstoff gesammelt und mittels des Entlastungskanals 51 abgeführt, um nicht in das schmierölgefüllte Reglergehäuse zu gelangen (Leckkraftstoffrückführung).The second shaft part 39 itself is mounted in a central bore 45 of a bearing bush 46, which is inserted in the housing bore receiving this end shield and is held by a screw 47. Between the housing 1 and this bearing bush 46 are two rings 48 available. An oil ring groove 49 is arranged in the central bore 45, from which a relief channel 51 branches off. This second shaft part 39 is guided in the central bore 45 with very little play, as is the case, for example, when guiding the pump piston in the cylinder. The oil ring groove 49 collects the fuel that may still leak through from the main suction chamber 10 and discharges it via the relief channel 51 in order not to get into the regulator housing filled with lubricating oil (leakage fuel return).

Das andere freie Ende, ein Wellenende 54 des ersten Wellenteils 38, ist in einer Sackbohrung 52 des als Lagerdeckel 53 ausgebildeten zweiten Lagerschildes 11 gelagert. Das Wellenende 54 weist hierfür einen Zapfen 54a auf, der ebenfalls ballig ausgebildet ist, um für die Lagerung nur Linienberührung aufzuweisen, so daß leichte Verbiegungen des Wellenteils 38 oder eine nicht exakt fluchtende Einbaulage des Lagerdeckels 53 zu keinen zusätzlichen Reibkräften führen.The other free end, a shaft end 54 of the first shaft part 38, is mounted in a blind bore 52 of the second bearing plate 11 designed as a bearing cover 53. For this purpose, the shaft end 54 has a pin 54a, which is also crowned to have only line contact for storage, so that slight bending of the shaft part 38 or an incorrectly aligned installation position of the bearing cover 53 does not lead to any additional frictional forces.

Die axiale Lage des ersten Wellenteils 38 ist durch einen Stift 55 gesichert, der in eine Ringnut 56 des Wellenteils 38 greift und im Lagerdeckel 53 angeordnet ist. Für die Montage des ersten Wellenteils 38 in der Sackbohrung 52 des Lagerdeckels 53 ist an dem Wellenende 54 zwischen Ringnut 56 und Zapfen 54a eine Abflachung 57 vorhanden, die etwa die Teife der Ringnut 56 erreicht. Hierdurch ist es möglich, an der Stelle der Abflachung 57 dieses freie Ende des ersten Wellenteils 38 in die Sackbohrung 52 zu schieben, um danach bajonettartig das Wellenteil 38 so zu verdrehen, daß der Stift 55 in die Ringnut 56 greift. Der Lagerdeckel 53 ist durch Schrauben 58 am Gehäuse befestigt. Die Montage der Verdrehwelle 12 wird wie folgt vorgenommen: Zuerst wird der erste Teil 38 der Verdrehwelle in das Pumpengehäuse eingeschoben, und zwar um 90 Grad gegenüber der Betriebslage verdreht. Danach wird diese Welle wieder um die 90 Grad in die Arbeislage zurückgedreht und mit den Mitnahmezapfen 14a in die Nuten 13 der Steuerschieber 9 eingesteckt. Danach werden die beiden Lagerschilde montiert, nämlich der Lagerdeckel 53 in der beschriebenen Art durch bajonettartiges Verdrehen, sodann die Lagerbuchse 46 mit bereits eingebauten zweiten Wellenteil 39.The axial position of the first shaft part 38 is secured by a pin 55 which engages in an annular groove 56 of the shaft part 38 and is arranged in the bearing cover 53. For the assembly of the first shaft part 38 in the blind bore 52 of the bearing cover 53, a flattening 57 is present on the shaft end 54 between the ring groove 56 and the pin 54a, which reaches approximately the same depth as the ring groove 56. This makes it possible to push this free end of the first shaft part 38 into the blind bore 52 at the location of the flattened portion 57 in order to then turn the shaft part 38 in a bayonet-like manner so that the pin 55 engages in the annular groove 56. The bearing cover 53 is fastened to the housing by screws 58. The rotation shaft 12 is assembled as follows: First, the first part 38 of the rotation shaft is pushed into the pump housing, namely rotated by 90 degrees with respect to the operating position. Then this shaft is rotated back into the working position by 90 degrees and inserted with the driving pins 14a into the grooves 13 of the control slide 9. Then the two end shields are mounted, namely the bearing cover 53 in the manner described by bayonet-like turning, then the bearing bush 46 with the second shaft part 39 already installed.

Claims (8)

1. Fuel injection pump for internal combustion engines, comprising a plurality of pump elements which are arranged in line in a pump housing (1), are driven by a common camshaft (6), each have one pump plunger (3) and one cylinder liner (2) and define a pump working chamber (18), a control slide (9) which is axially displaceable on each pump plunger (3) and controls at least one control port (24) in connection with a central blind bore (22), open towards the pump working chamber (18), of the pump plunger (3) and leading into the circumferential surface of the pump plunger (3), a suction chamber (8, 10) which surrounds the individual control slides (9), is defined by the pump housing and through which fuel of low pressure flows, and a rotary shaft (12) which is provided for the simultaneous actuation of all control slides (9) for the start or end of delivery, is double mounted in the pump housing and is coupled to the control slides (9) via adjustable driving studs (14), characterized in that the rotary shaft (12) is split between the bearings (11), namely into a first shaft part (38), carrying the driving studs (14a) and rotatably mounted with its free end in the pump housing (1), and a second shaft part (39) which is coupled to the first shaft part (38) in such a way as to be fixed in terms of rotation and is also mounted in a sealing manner in the pump housing (1) and forms a radial guide (40, 41) for the end of the first shaft part (38) facing it, and in that the one shaft part (39), on the coupling side, has as a radial guide a slightly barrelled end journal (41) which runs in the shaft axis and is mounted in a corresponding blind bore (40) on the front end of the other shaft part (38).
2. Fuel injection pump according to Claim 1, characterized in that the shaft parts (38, 39), at the front ends facing one another, each have a radially widened section (42) where there are driving claws (43) or driving recesses (44) for the non-rotational connection.
3. Fuel injection pump according to either of the preceding claims, characterized in that the second shaft part (39) is mounted in a central bore (45) of a bearing bush (46) which is arranged in a pump housing bore by means of sealing rings (48) in such a way as to provide a radial seal, and in that an annular oil groove (49) having a relief channel (51) for the return of leakage fuel is present in the central bore (45).
4. Fuel injection pump according to Claim 3, characterized in that the second shaft part (39) is guided in the central bore (45) like a pump- element seal used in injection pumps.
5. Fuel injection pump according to any of the preceding claims, characterized in that a shaft end (54), at the free end of the first shaft part (38), runs in a blind bore (52) of a bearing cap (53) inserted in a bore of the pump housing (1).
6. Fuel injection pump according to Claim 5, characterized in that a journal (54a) located at the shaft end (54) is of barrelled design.
7. Fuel injection pump according to Claim 5 or 6, characterized in that there is an annular groove (56) in the shaft end (54) plunging into the blind bore (52), into which annular groove (56) a locking pin (55), arranged in the bearing cap (53), engages in order to prevent axial displacement of the first shaft part (38).
8. Fuel injection pump according to Claim 7, characterized in that the shaft end (54) has a flat (57) down to about the annular groove root so that, after this shaft end has been pushed into the blind bore (52) and this flat (57) has been pushed past the pin (55), axial anchoring takes place by rotating the first shaft part (38) in a bayonet-like way relative to the bearing cap (53).
EP87901395A 1986-03-22 1987-03-19 Fuel injection pump for internal combustion engines Expired - Lifetime EP0261154B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3609760 1986-03-22
DE3609760 1986-03-22
DE3630799 1986-09-10
DE19863630799 DE3630799A1 (en) 1986-03-22 1986-09-10 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0261154A1 EP0261154A1 (en) 1988-03-30
EP0261154B1 true EP0261154B1 (en) 1990-05-30

Family

ID=25842233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901395A Expired - Lifetime EP0261154B1 (en) 1986-03-22 1987-03-19 Fuel injection pump for internal combustion engines

Country Status (7)

Country Link
US (1) US4842497A (en)
EP (1) EP0261154B1 (en)
JP (1) JPS63502915A (en)
KR (1) KR880701327A (en)
BR (1) BR8706767A (en)
DE (2) DE3630799A1 (en)
WO (1) WO1987005664A1 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844430A1 (en) * 1988-12-31 1990-07-05 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4041503C2 (en) * 1990-12-22 2001-02-15 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
DE4140759A1 (en) * 1991-12-11 1993-06-17 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4143040C1 (en) * 1991-12-24 1993-07-08 Robert Bosch Gmbh, 7000 Stuttgart, De
DE4227854B4 (en) * 1992-08-22 2005-12-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
DE19712872A1 (en) * 1997-03-27 1998-10-01 Bosch Gmbh Robert Pump, in particular high-pressure pump for a fuel injection device of an internal combustion engine
JP2000130279A (en) * 1998-10-21 2000-05-09 Toyota Motor Corp High-pressure fuel supplying device of internal combustion engine
US6871629B2 (en) * 2001-07-31 2005-03-29 Thermo King Corporation Refrigeration system with low-fuel shutdown
US7311087B2 (en) * 2004-11-23 2007-12-25 Cummins Inc. Fuel pump with a guided tappet assembly and methods for guiding and assembly
GB2554731B (en) * 2016-10-07 2019-04-03 Caterpillar Motoren Gmbh & Co Piston pump having push rod assembly and stopping assembly

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Publication number Priority date Publication date Assignee Title
US2110314A (en) * 1934-12-03 1938-03-08 Citroen Sa Andre Pump for injection engines
US3385221A (en) * 1967-03-07 1968-05-28 Caterpillar Tractor Co Multi-plunger engine fuel oil pump
FR1585785A (en) * 1968-10-10 1970-01-30
US3667437A (en) * 1970-08-19 1972-06-06 Allis Chalmers Mfg Co Multiple plunger fuel injection pump
GB2042629B (en) * 1979-02-17 1983-01-06 Lucas Industries Ltd Fuel pumping apparatus
EP0027790A1 (en) * 1979-10-15 1981-04-29 Friedmann & Maier Aktiengesellschaft Injection pump
DE3442953A1 (en) * 1983-12-12 1985-06-20 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
US4576130A (en) * 1984-11-24 1986-03-18 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
WO1987005664A1 (en) 1987-09-24
DE3630799A1 (en) 1987-09-24
US4842497A (en) 1989-06-27
EP0261154A1 (en) 1988-03-30
JPS63502915A (en) 1988-10-27
KR880701327A (en) 1988-07-26
DE3762984D1 (en) 1990-07-05
BR8706767A (en) 1988-02-23

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