EP0262167B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

Info

Publication number
EP0262167B1
EP0262167B1 EP87901394A EP87901394A EP0262167B1 EP 0262167 B1 EP0262167 B1 EP 0262167B1 EP 87901394 A EP87901394 A EP 87901394A EP 87901394 A EP87901394 A EP 87901394A EP 0262167 B1 EP0262167 B1 EP 0262167B1
Authority
EP
European Patent Office
Prior art keywords
sliding shoe
pin
pump
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
EP87901394A
Other languages
German (de)
French (fr)
Other versions
EP0262167A1 (en
Inventor
Josef Güntert
Walter Häfele
Manfred KRÄMER
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 EP0262167A1 publication Critical patent/EP0262167A1/en
Application granted granted Critical
Publication of EP0262167B1 publication Critical patent/EP0262167B1/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
    • 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
    • F02M59/20—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

Definitions

  • the invention relates to a fuel injection pump according to the preamble of claim 1.
  • the axial position of the control slide usually determines the start or end of spraying.
  • the injection quantity is controlled by the axial position of the control slide.
  • an inaccurate axial position of the control slide has a detrimental effect on the injection quality, which has an immediate effect on the combustion, with the result that the engine runs out of round due to the injection not being timely or that it is too fast or too fast due to the inaccurate metering quantity runs slowly.
  • the adjusting pin engages with a spherical head in the transverse groove of the control slide, so that there is a point-like contact between the head and the groove surfaces, which results in a long running time and high shaking load on these actuating elements premature wear and thus an undesired play between the head and the groove surfaces leads to the corresponding errors in the fuel control.
  • the installation position of the adjustment bolt is determined during the adjustment, because due to the eccentric arrangement of the head, the stroke position of the control slide is adjusted by turning the adjustment bolt with subsequent countering.
  • the game resulting from wear and tear nullifies this adjustment, with the consequences already mentioned.
  • the adjusting bolt is arranged in a rotationally fixed manner on a clamping ring which serves as a fastening part and which clamps around the round torsion shaft.
  • the required adjustment can be made relatively easily by rotating the clamp on the rotating shaft, but there is also the disadvantage mentioned above, in addition to other disadvantages, that the force transmission between adjusting bolts and associated surfaces of the transverse groove takes place in a punctiform manner, since the adjusting bolt is designed as a rotating part. Due to the only point-like contact, there is correspondingly rapid and severe wear on the adjusting bolt and on the associated groove surfaces.
  • this sliding part of the adjusting arm has a cylindrical cross section with a flattened end face in a plane which runs through a center line of the sliding part which projects radially from the rotating shaft and at right angles to the axis of the rotating shaft, the curved contact surfaces of which lie opposite the working surfaces of the transverse groove.
  • the line contact sought with this construction can, however, only be achieved ideally with surfaces of the transverse groove and the sliding part lying absolutely parallel to one another, which is hardly possible in practice.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the wear due to the line contact between the slide shoe and transverse groove surface is significantly less, so that not only a longer life of these transmission elements can be achieved, but also a much better quality of fuel control.
  • the slide shoe is secured against axial displacement on the pin, which can advantageously be done according to one of claims 3, 4 or 5 by a pin arranged parallel to the contact surfaces of the slide shoe in the slide shoe, which in a Pin arranged annular groove or cross hole or tangential transverse groove engages.
  • FIG. 1 shows a vertical section through a fuel injection pump according to the invention
  • FIG. 2 shows an enlarged view of the adjusting bolt Scale
  • Figure 3 is an end view of the adjusting bolt according to arrow 111-111 in Figure 2, the first embodiment
  • Figures 4 and 5 show views corresponding to Figures 2 and 3, but for the second embodiment and with a dash-dotted design variant for securing the position of the sliding block.
  • the fuel injection pump shown is a multi-cylinder pump, of which only one pump element is shown in the vertical section according to FIG. 1.
  • a cylinder liner 2 is embedded in a housing 1, in which a pump piston 3 is driven by a camshaft 6 with the interposition of a roller tappet 4 with roller 5 against the force of a spring 7 for its axial movement forming the working stroke.
  • a recess 8 is provided in the cylinder liner 2, in which a control slide 9 is axially displaceable on the pump piston 3.
  • the recess 8 of the cylinder liner 2 is connected to a suction chamber 10, in which a rotating shaft 12 is arranged, through which the individual control slides 9, only one of which is shown, are axially displaced.
  • a rotating shaft 12 In cross bores 41 of the rotating shaft 12 there are radially protruding adjusting bolts 14 which engage in a transverse groove 13 of the control slide 9, of which only one is also shown, which is fixed in its position on the rotating shaft 12 by means of a clamping nut 15 serving as a fastening part.
  • a plug 16 is provided in the housing 1 opposite each of these clamping nuts 15, after removal of which an adjustment of the individual adjusting bolts 14 is possible by first loosening the clamping nut 15, then turning the adjusting bolt 14 for the adjustment, and then by the clamping nut 15 to be committed again.
  • the individual control slides 9 of the injection pump can be coordinated with one another in their axial position, since in the first exemplary embodiment the adjusting bolts 14 are eccentric bolts, as explained in more detail below.
  • 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 has been covered.
  • a guide pin 26 is inserted in a fitting groove 11 provided in the surface area of the cylinder liner 2, which pin is inserted into a longitudinal groove 27 of the control slide 9 engages.
  • the pump piston 3 has a flattened portion 28 on its lower section, on which a driving member 31, which can be rotated in a known manner by a control rod 29, engages, so that an axial displacement of the control rod 29 causes the pump piston 3 to rotate 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 pump elements takes place via an inflow channel 33.
  • the fuel not being injected flows out of the recesses 8 into the suction chamber 10 and from there via a drain, not shown, into a return line and to the fuel tank or a feed pump of the injection pump, also not shown.
  • the cylinder liner 2 has a flange 34 with which it is clamped to the housing 1 by bolts 35 and nuts 36.
  • the common plane passing through the central axes of the bolts 35 is rotated by approximately 30 ° with respect to the sectional plane through the housing 1 in FIG.
  • the bolts 35 engage in bores which are no longer shown here and which are provided in the area between two pump elements in relation to the longitudinal extent of the pump in the pump housing 1.
  • the adjusting bolt 14 is shown in an enlarged view.
  • This adjusting bolt 14 has a pin 37, which is arranged eccentrically on a cheek 38, which in turn extends coaxially to a bearing section 39 which is fitted into one of the transverse bores 41 of the rotating shaft 12.
  • a threaded section 42 is provided on this adjusting bolt 14, which carries the clamping nut 15, so that when the clamping nut 15 is screwed tight, the cheek 38 is clamped to the rotating shaft 12 in such a way that this adjusting bolt 14 is prevented from rotating in the rotating shaft 12.
  • the eccentric pin 37 has a cylindrical outer surface 43, on which a sliding block 44 is inserted by means of a central bore 40.
  • This slide shoe 44 is secured against axial displacement by a pin 45, this pin 45 engaging in an annular groove 46 of the pin 37. Rotation of the slide shoe 44 on the pin 37 is thus possible.
  • the pin 45 is fastened parallel to the contact surfaces 51 and tangentially to the wall of the central bore 40 of the slide shoe 44 or to the cylindrical outer surface 43 of the pin 37 in the slide shoe 44.
  • the ends 47 of the pin 45 protrude beyond the side surfaces 48 of the slide shoe 44 and are angled in order to prevent the pin 45 from falling out.
  • the surfaces 51 of the sliding block 44 which cooperate with the working surfaces 49 of the groove 13 are curved so that a cylindrical cross section of the sliding block 44 with flattened end faces 50 is formed (FIG. 2) and a linear contact between the working surfaces 49 and the surfaces also referred to as contact surfaces 51 is guaranteed.
  • the fuel injection pump shown in Figures 1 to 3 works as follows: During at least part of the suction stroke of the pump piston 3 and in the area of the bottom dead center of its stroke movement flows out of the suction chamber 10 via the oblique grooves 24, the transverse bore 23 and the blind bore 22 and the suction bore 32 fuel into the pump work chamber 18. In the subsequent pressure stroke of the pump piston 3 caused by camshaft 6, roller 5 and roller tappet 4, the pressure required for the injection builds up in the pump work chamber 18 only when these inflow channels between the suction chamber 10 and the Pump work space 18 are locked. As long as fuel flows back out of the pump work space 18 via these channels back into the suction space 10.
  • the high pressure required for the injection builds up in the pump work space 18 and the delivery to the internal combustion engine begins with the injection.
  • the pump working chamber 18 is connected to the suction chamber 10 by the inclined grooves 24 coming into overlap with the radial bores 25, so that the fuel which is conveyed on is driven off under high pressure.
  • This effective injection stroke of the pump piston 3 depends on its rotational position, which is determined by the control rod 29. Depending on the rotational position, the distance of the oblique grooves 24 from the radial bores 25 determined thereby is different, which corresponds to an injection stroke of different lengths.
  • the axial position of the control slide 9, determines the start of the high-pressure injection with respect to the rotational position of the camshaft 6.
  • the second embodiment shown in Figures 4 and 5 with a dash-dotted design variant differs essentially from the previously described first embodiment in a changed, only a limited rotatability to secure the position of the shoe and by the differently designed, non-rotatable by means of a mounting bracket on the Twist shaft mounted adjustment bolt.
  • the same parts are provided with the same reference symbols, different parts with a reference symbol increased by 100 and new parts with new reference symbols.
  • the adjusting bolt 114 of the second exemplary embodiment carries, like the adjusting bolt 14 of the first exemplary embodiment, the cylindrical pin 137 carrying the sliding shoe 144 at its end portion engaging in the transverse groove 13 of the control slide 9.
  • the adjusting bolt 114 is on a fastening part designed as a U-shaped bracket 115 attached and z. B. fixed by brazing in its position.
  • the pin 45 which is arranged parallel to the contact surfaces 51 in the slide shoe 144 and is inserted through a transverse bore 52 crossing the longitudinal axis of the pin 137 in the pin 137, is provided.
  • the position of the pin 45 is also fixed here by angling its free ends 47.
  • the diameter of the transverse bore 52 is now chosen to be larger than the diameter of the pin 45 in such a way that a twisting play of the sliding block 144 limited to a few angular degrees, preferably +/- 5 ° in both directions of rotation, is possible.
  • This limited backlash serves firstly to compensate for misalignments and thus prevents jamming and jamming of the components involved in the control of the slide position; and secondly, the slide shoe 144 is prevented from turning away from its installation position provided for the actuation of the control slide 9 when the twisting shaft 12 is inserted.
  • a so-called "blind assembly” is possible, ie the slide shoes 144 mounted on the adjustment bolts 114 previously set in their installed position with respect to the rotating shaft 12 center themselves during assembly in the transverse grooves 13 of the control slide 9 receiving them, with the help of her arched celebrity approximately 51 and the fact that they can only turn a few degrees from the final installation position.
  • the aforementioned setting which is to be carried out outside the controller housing, of the installation position of the adjusting bolts 114, which is responsible for the correct stroke position of the control slide 9, is set by exchanging intermediate plates of different thicknesses between two opposing surfaces on the torsion shaft 12 and the fastening part 115, but is not the subject of the present case Invention.
  • the pin 45 assumes the same position as in the first exemplary embodiment according to FIGS. 1 to 3.
  • the pin 45 traverses the slide shoe 144 parallel to its contact surfaces 51 and tangentially to the wall of the central bore 40 in the slide shoe 144.
  • the lateral surface 43 of the pin 137 on the adjusting bolt 114 has a rectified transverse groove 53, into which the pin 45 engages with a slight lateral but somewhat enlarged distance from the groove base 53a.
  • This distance between the pin 45 and the groove base 53a is dimensioned such that the previously described twisting play of the sliding block 144, which is limited to a few angular degrees, is ensured.
  • this securing of the position of the sliding shoe 144 allows the greatest possible reduction in the axial play while maintaining the torsional play.

Abstract

Fuel injection pump as described, with at least one pump element composed of a cylinder liner (2) and one pump piston (3) and with one control slide (9) on the pump piston (3), which piston can be rotated in order to control the fuel. The control slide (9) can be slid axially in order to modify the initiation of injection, the axial movement being effected by means of a shaft (12) mounted in the pump housing (1), on which at least one adjustment pin (14) can be clamped by means of a securing part (lock-nut 15) in its installation position, after the adjustment has been made. An eccentric lug (37) of the eccentric pin (14) is of cylindrical design, and a sliding shoe (44) can be inserted on the lug (37) by means of a central drilling (40). Said sliding shoe has a rectangular shape with convex contact surfaces (51) in order to ensure a linear contact between the sliding shoe (44) and groove (13), and it is prevented from falling off by means of a pin (45).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe nach der Gattung des Patentanspruchs 1.The invention relates to a fuel injection pump according to the preamble of claim 1.

Bei diesen schiebergesteuerten Kraftstoffeinspritzpumpen bestimmt meist die axiale Lage des Steuerschiebers den Spritzbeginn bzw. das Spritzende. Es gibt aber auch derartige Pumpen, bei denen durch die axiale Lage des Steuerschiebers die Einspritzmenge gesteuert wird. In jedem Fall wirkt sich eine ungenaue axiaie Position des Steuerschiebers nachteilig auf die Einspritzqualität aus, was sich unmittelbar auf die Verbrennung auswirkt, mit der Folge, daß der Motor aufgrund der nicht zeitgerechten Einspritzung unrund läuft oder daß er aufgrund der ungenauen Zumeßmenge zu schnell oder zu langsam läuft.In these slide-controlled fuel injection pumps, the axial position of the control slide usually determines the start or end of spraying. However, there are also pumps of this type in which the injection quantity is controlled by the axial position of the control slide. In any case, an inaccurate axial position of the control slide has a detrimental effect on the injection quality, which has an immediate effect on the combustion, with the result that the engine runs out of round due to the injection not being timely or that it is too fast or too fast due to the inaccurate metering quantity runs slowly.

Bei einer bekannten Kraftstoffeinspritzpumpe dieser Art (EP-A 0 181 402) greift der Verstellbolzen mit einem kugeligen Kopf in die Quernut des Steuerschiebers, so daß eine punktförmige Berührung zwischen Kopf und Nutenflächen entsteht, die bei der großen Laufdauer und hohen Schüttelbelastung dieser Betätigungselemente zu einer vorzeitigen Abnutzung und damit zu einem ungewünschten Spiel zwischen Kopf und Nutenflächen führt mit den entsprechenden Fehlern bei der Kraftstoffsteuerung. Die Einbaulage des Verstellbolzens wird bei der Justierung festgelegt, da wegen der exzentrischen Anordnung des Kopfes die Justierung der Hublage des Steuerschiebers durch Verdrehen des Verstellbolzens mit anschließendem Kontern erfolgt. Das durch Abnutzung entstehende Spiel macht aber diese Justierung zunichte, mit den bereits genannten Folgen.In a known fuel injection pump of this type (EP-A 0 181 402), the adjusting pin engages with a spherical head in the transverse groove of the control slide, so that there is a point-like contact between the head and the groove surfaces, which results in a long running time and high shaking load on these actuating elements premature wear and thus an undesired play between the head and the groove surfaces leads to the corresponding errors in the fuel control. The installation position of the adjustment bolt is determined during the adjustment, because due to the eccentric arrangement of the head, the stroke position of the control slide is adjusted by turning the adjustment bolt with subsequent countering. However, the game resulting from wear and tear nullifies this adjustment, with the consequences already mentioned.

Bei einer anderen bekannten Kraftstoffeinspritzpumpe dieser Art (DE-A35 22 414) ist der Verstellbolzen drehfest an einem als Befestigungsteil dienenden Spannring angeordnet, der schellenartig die runde Verdrehwelle umspannt. Die erforderliche Justierung ist zwar durch Verdrehen der Schelle auf der Verdrehwelle relativ leicht vornehmbar, doch besteht auch hier neben anderen Nachteilen der bereits erwähnte Nachteil, daß die Kraftübertragung zwischen Verstellbolzen und zugeordneten Flächen der Quernut punktförmig erfolgt, da der Verstellbolzen als Drehteil ausgebildet ist. Aufgrund der nur punktförmigen Berührung entsteht somit auch hier eine entsprechend schnelle und starke Abnutzung am Verstellbolzen sowie an den zugeordneten Nutflächen.In another known fuel injection pump of this type (DE-A35 22 414), the adjusting bolt is arranged in a rotationally fixed manner on a clamping ring which serves as a fastening part and which clamps around the round torsion shaft. The required adjustment can be made relatively easily by rotating the clamp on the rotating shaft, but there is also the disadvantage mentioned above, in addition to other disadvantages, that the force transmission between adjusting bolts and associated surfaces of the transverse groove takes place in a punctiform manner, since the adjusting bolt is designed as a rotating part. Due to the only point-like contact, there is correspondingly rapid and severe wear on the adjusting bolt and on the associated groove surfaces.

In der nachveröffentlichten, als ältere Patentanmeldung zu wertenden EP-A-0 207 283 ist eine Kraftstoffeinspritzpumpe beschrieben, die nahezu alle gattungsbildenden Merkmale aufweist. Lediglich anstelle des in die Quernut des Steuerschiebers eingreifenden Verstellbolzens ist auf der Verdrehwelle ein Verstellarm befestigt. der an seinem äußersten Ende einen Gleitteil aufweist. der in jeder Betriebslage, parallel zu den Längsachsen der Pumpenkolben und der Verdrehwelle jeweils eine rechteckige Form hat, so daß zumindest theoretisch zwischen Gleitteil und Quernut in beiden Verstellrichtungen des Steuerschiebers eine Linienberührung möglich ist. Überdies weist dieser Gleitteil des Verstellarms in einer Ebene, die durch eine radial von der Verdrehwelle abstehende Mittellinie des Gleitteils hindurch und rechtwinklig zur Achse der Verdrehwelle verläuft, einen zylinderförmigen Querschnitt mit abgeflachter Stirnfläche auf, dessen gewölbte Berührungsflächen den Arbeitsflächen der Quernut gegenüberliegen. Die mit dieser Konstruktion angestrebte Linienberührung kann aber nur im Idealfall bei absolut parallel zueinanderliegenden Flächen der Quernut und des Gleitteils verwirklicht werden, was in der Praxis kaum möglich ist.In the post-published EP-A-0 207 283, which is to be regarded as an earlier patent application, a fuel injection pump is described which has almost all generic features. An adjusting arm is only attached to the rotating shaft instead of the adjusting bolt which engages in the transverse groove of the control slide. which has a sliding part at its extreme end. which has a rectangular shape in each operating position, parallel to the longitudinal axes of the pump pistons and the torsion shaft, so that a line contact is possible at least theoretically between the sliding part and the transverse groove in both adjustment directions of the control slide. In addition, this sliding part of the adjusting arm has a cylindrical cross section with a flattened end face in a plane which runs through a center line of the sliding part which projects radially from the rotating shaft and at right angles to the axis of the rotating shaft, the curved contact surfaces of which lie opposite the working surfaces of the transverse groove. The line contact sought with this construction can, however, only be achieved ideally with surfaces of the transverse groove and the sliding part lying absolutely parallel to one another, which is hardly possible in practice.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß aufgrund der Linienberührung zwischen Gleitschuh und Quernutfläche die Abnutzung wesentlich geringer ist, so daß nicht nur eine längere Lebensdauer dieser Übertragungsglieder erzielbar ist, sondern auch eine wesentlich bessere Qualität der Kraftstoffsteuerung.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the wear due to the line contact between the slide shoe and transverse groove surface is significantly less, so that not only a longer life of these transmission elements can be achieved, but also a much better quality of fuel control.

Nach einer weiteren Ausgestaltung der Erfindung ist der Gleitschuh gemäß Anspruch 2 gegen axiales Verschieben auf dem Zapfen gesichert, was vorteilhafterweise gemäß einem der Ansprüche 3, 4 oder 5 durch einen parallel zu den Berührungsflächen des Gleitschuhs im Gleitschuh angeordneten Stift erfolgen kann, der in eine im Zapfen angeordnete Ringnut bzw. Querbohrung oder tangentiale Quernut greift. Hierdurch ist in sehr einfacher Weise eine Axialsicherung gegeben, die nicht nur in der Herstellung günstig ist, sondern auch ein Minimum an Reibung zwischen Zapfen und Gleitschuh verursacht. Im Falle des in bekannter Weise (DE-A-35 22 414) drehfest über ein Befestigungsteil mit der Verdrehwelle verbundenen Verstellbolzens und des gemäß den kennzeichnenden Merkmalen der Ansprüche 4 und 5 zur Lagesicherung in die Querbohrung oder Quernut am Zapfen eingreifenden Stiftes verhindert das begrenzte Verdrehspiel ein Verkanten und Klemmen des Gleitschuhs und erleichtert die "blinde Montage", da sich der Gleitstein nicht unzulässig stark aus seiner Einbaulage verdrehen kann und somit leicht in die Quernut des Steuerschiebers eingeführt werden kann.According to a further embodiment of the invention, the slide shoe is secured against axial displacement on the pin, which can advantageously be done according to one of claims 3, 4 or 5 by a pin arranged parallel to the contact surfaces of the slide shoe in the slide shoe, which in a Pin arranged annular groove or cross hole or tangential transverse groove engages. This provides axial securing in a very simple manner, which is not only inexpensive to manufacture, but also causes a minimum of friction between the pin and the sliding block. In the case of in a known manner (DE-A-35 22 414) non-rotatably connected via a fastening part with the twist shaft adjusting bolt and engaging according to the characterizing features of claims 4 and 5 for securing the position in the transverse bore or transverse groove on the pin prevents the limited backlash tilting and jamming of the slide shoe and facilitates "blind assembly" since the slide block cannot twist out of its installation position to an unacceptable extent and can therefore be easily inserted into the transverse groove of the control slide.

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

Zeichnungdrawing

Zwei Ausführungsbeispiele des Gegenstandes der Erfindung sind mit einer zusätzlichen Ausführungsvariante in der Zeichnung dargestellt und im folgenden näher beschrieben. Es zeigen Figur 1 einen Vertikalschnitt durch eine erfindungsgemäße Kraftstoffeinspritzpumpe, Figur 2 eine Ansicht des Verstellbolzens in vergrößertem Maßstab und Figur 3 eine Stirnseitenansicht des Verstellbolzens entsprechend Pfeil 111-111 in Figur 2, des ersten Ausführungsbeispiels; und die Figuren 4 und 5 zeigen Ansichten entsprechend den Figuren 2 und 3, jedoch für das zweite Ausführungsbeispiel und mit einer strichpunktiert eingezeichneten Ausführungsvariante zur Lagesicherung des Gleitschuhs.Two embodiments of the subject matter of the invention are shown with an additional embodiment variant in the drawing and described in more detail below. FIG. 1 shows a vertical section through a fuel injection pump according to the invention, FIG. 2 shows an enlarged view of the adjusting bolt Scale and Figure 3 is an end view of the adjusting bolt according to arrow 111-111 in Figure 2, the first embodiment; and Figures 4 and 5 show views corresponding to Figures 2 and 3, but for the second embodiment and with a dash-dotted design variant for securing the position of the sliding block.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der dargestellten Kraftstoffeinspritzpumpe handelt es sich um eine Mehrzylinderpumpe, von der im Vertikalschnitt nach Figur 1 nur ein Pumpelement dargestellt ist. So ist in einem Gehäuse 1 eine Zylinderbüchse 2 eingelassen, in der 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. In der Zylinderbüchse 2 ist eine Aussparung 8 vorgesehen, in der auf dem Pumpenkolben 3 axial verschiebbar ein Steuerschieber 9 vorhanden ist.The fuel injection pump shown is a multi-cylinder pump, of which only one pump element is shown in the vertical section according to FIG. 1. A cylinder liner 2 is embedded in a housing 1, in which a pump piston 3 is driven by a camshaft 6 with the interposition of a roller tappet 4 with roller 5 against the force of a spring 7 for its axial movement forming the working stroke. A recess 8 is provided in the cylinder liner 2, in which a control slide 9 is axially displaceable on the pump piston 3.

Die Aussparung 8 der Zylinderbüchse 2 ist mit einem Saugraum 10 verbunden, in dem eine Verdrehwelle 12 angeordnet ist, durch die die einzelnen Steuerschieber 9, von denen nur einer dargestellt ist, axial verschoben werden. In Querbohrungen 41 der Verdrehwelle 12 sind radial herausragende und in eine Quernut 13 des Steuerschiebers 9 greifende Verstellbolzen 14 vorhanden, von denen ebenfalls nur einer dargestellt ist, der mittels einer als ein Befestigungsteil dienenden Spannmutter 15 in seiner Lage an der Verdrehwelle 12 fixiert ist. Im Gehäuse 1 ist jeweils gegenüber diesen Spannmuttern 15 ein Verschlußstopfen 16 vorgesehen, nach dessen Entfernen eine Justierung der einzelnen Verstellbolzen 14 möglich ist, indem zuerst die Spannmutter 15 gelockert wird, danach der Verstellbolzen 14 für die Justierung verdreht wird, um dann durch die Spannmutter 15 wieder festgelegt zu werden. Auf diese Weise können die einzelnen Steuerschieber 9 der Einspritzpumpe in ihrer axialen Lage aufeinander abgestimmt werden, da im ersten Ausführungsbeispiel die Verstellbolzen 14, wie weiter hinten näher ausgeführt, Exzenterbolzen sind.The recess 8 of the cylinder liner 2 is connected to a suction chamber 10, in which a rotating shaft 12 is arranged, through which the individual control slides 9, only one of which is shown, are axially displaced. In cross bores 41 of the rotating shaft 12 there are radially protruding adjusting bolts 14 which engage in a transverse groove 13 of the control slide 9, of which only one is also shown, which is fixed in its position on the rotating shaft 12 by means of a clamping nut 15 serving as a fastening part. A plug 16 is provided in the housing 1 opposite each of these clamping nuts 15, after removal of which an adjustment of the individual adjusting bolts 14 is possible by first loosening the clamping nut 15, then turning the adjusting bolt 14 for the adjustment, and then by the clamping nut 15 to be committed again. In this way, the individual control slides 9 of the injection pump can be coordinated with one another in their axial position, since in the first exemplary embodiment the adjusting bolts 14 are eccentric bolts, as explained in more detail below.

Der Pumpenkolben 3 der Zylinderbüchse 2 und ein Druckventil 17, das in die Zylinderbüchse 2 eingesetzt ist, 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, welche 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.The pump piston 3 of the cylinder liner 2 and a pressure valve 17, which is inserted into the cylinder liner 2, 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 work 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 has been covered.

Damit der Steuerschieber 9 bei seiner axialen Verschiebung auf dem Pumpenkolben 3 gegen Verdrehen gesichert und eine exakte Zuordnung von Schrägnuten 24 und Radialbohrungen 25 gewährleistet ist, ist in einer in der Mantelfäche der Zylinderbüchse 2 vorgesehenen Paßnut 11 ein Führungsstift 26 eingesetzt, der in eine Längsnut 27 des Steuerschiebers 9 greift.So that the control slide 9 is secured against rotation during its axial displacement on the pump piston 3 and an exact assignment of oblique grooves 24 and radial bores 25 is ensured, a guide pin 26 is inserted in a fitting groove 11 provided in the surface area of the cylinder liner 2, which pin is inserted into a longitudinal groove 27 of the control slide 9 engages.

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.The pump piston 3 has a flattened portion 28 on its lower section, on which a driving member 31, which can be rotated in a known manner by a control rod 29, engages, so that an axial displacement of the control rod 29 causes the pump piston 3 to rotate 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. Die Kraftstoffversorgung der einzelnen Pumpenelemente erfolgt über einen Zuströmkanal 33. Der nicht zur Einspritzung gelangende Kraftstoff strömt aus den Aussparungen 8 in den Saugraum 10 und von dort über einen nicht dargestellten Abfluß in eine Rücklaufleitung und zu dem Kraftstofftank oder einer ebenfalls nicht dargestellten Vorförderpumpe der Einspritzpumpe.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). The fuel supply to the individual pump elements takes place via an inflow channel 33. The fuel not being injected flows out of the recesses 8 into the suction chamber 10 and from there via a drain, not shown, into a return line and to the fuel tank or a feed pump of the injection pump, also not shown.

Die Zylinderbüchse 2 weist einen Flansch 34 auf, mit dem sie durch Bolzen 35 und Muttern 36 am Gehäuse 1 festgespannt ist. Die durch die Mittelachsen der Bolzen 35 gehende gemeinsame Ebene ist gegenüber der Schnittebene durch das Gehäuse 1 in Figur 1 um etwa 30° verdreht. Die Bolzen 35 greifen in hier nicht mehr dargestellte Bohrungen, welche in bezug auf die Längsausdehnung der Pumpe im Pumpengehäuse 1 im Bereich zwischen zwei Pumpenelementen vorgesehen sind.The cylinder liner 2 has a flange 34 with which it is clamped to the housing 1 by bolts 35 and nuts 36. The common plane passing through the central axes of the bolts 35 is rotated by approximately 30 ° with respect to the sectional plane through the housing 1 in FIG. The bolts 35 engage in bores which are no longer shown here and which are provided in the area between two pump elements in relation to the longitudinal extent of the pump in the pump housing 1.

In den Figuren 2 und 3 ist der Verstellbolzen 14 in vergrößerter Darstellung gezeigt. Dieser Verstellbolzen 14 weist einen Zapfen 37 auf, der exzentrisch an einer Wange 38 angeordnet ist, die wiederum achsgleich zu einem Lagerabschnitt 39 verläuft, welcher in eine der Querbohrungen 41 der Verdrehwelle 12 eingepaßt ist. Außerdem ist an diesem Verstellbolzen 14 ein Gewindeabschnitt 42 vorgesehen, der die Spannmutter 15 trägt, so daß bei Festschrauben der Spannmutter 15 die Wange 38 an die Verdrehwelle 12 so festgespannt wird daß ein Verdrehen dieses Verstellbolzens 14 in der Verdrehwelle 12 verhindert wird.In Figures 2 and 3, the adjusting bolt 14 is shown in an enlarged view. This adjusting bolt 14 has a pin 37, which is arranged eccentrically on a cheek 38, which in turn extends coaxially to a bearing section 39 which is fitted into one of the transverse bores 41 of the rotating shaft 12. In addition, a threaded section 42 is provided on this adjusting bolt 14, which carries the clamping nut 15, so that when the clamping nut 15 is screwed tight, the cheek 38 is clamped to the rotating shaft 12 in such a way that this adjusting bolt 14 is prevented from rotating in the rotating shaft 12.

Der exzentrische Zapfen 37 weist eine zylindrische Mantelfläche 43 auf, auf die mittels einer zentralen Bohrung 40 ein Gleitschuh 44 gesteckt ist. Dieser Gleitschuh 44 ist durch einen Stift 45 gegen axiales Verschieben gesichert, wobei dieser Stift 45 in eine Ringnut 46 des Zapfens 37 greift. Somit ist ein Verdrehen des Gleitschuhs 44 auf dem Zapfen 37 möglich. Der Stift 45 ist parallel zu den Berührungsflächen 51 und tangential zur Wandung der zentralen Bohrung 40 des Gleitschuhs 44 bzw. zur zylindrischen Mantelfläche 43 des Zapfens 37 im Gleitschuh 44 befestigt.The eccentric pin 37 has a cylindrical outer surface 43, on which a sliding block 44 is inserted by means of a central bore 40. This slide shoe 44 is secured against axial displacement by a pin 45, this pin 45 engaging in an annular groove 46 of the pin 37. Rotation of the slide shoe 44 on the pin 37 is thus possible. The pin 45 is fastened parallel to the contact surfaces 51 and tangentially to the wall of the central bore 40 of the slide shoe 44 or to the cylindrical outer surface 43 of the pin 37 in the slide shoe 44.

Wie Figur 3 zu entnehmen ist, ragen die Enden 47 des Stiftes 45 über die Seitenflächen 48 des Gleitschuhs 44 hinaus und sind, um ein Herausfallen des Stiftes 45 zu vermeiden, abgewinkelt. Die mit den Arbeitsflächen 49 der Nut 13 zusammenwirkenden Flächen 51 des Gleitschuhs 44 sind gewölbt ausgebildet, so daß ein zylinderförmiger Querschnitt des Gleitschuhs 44 mit abgeflachten Stirnflächen 50 entsteht (Figur 2) und eine linienförmige Berührung zwischen den Arbeitsflächen 49 und den auch als Berührungsflächen bezeichneten Flächen 51 gewährleistet ist.As can be seen in FIG. 3, the ends 47 of the pin 45 protrude beyond the side surfaces 48 of the slide shoe 44 and are angled in order to prevent the pin 45 from falling out. The surfaces 51 of the sliding block 44 which cooperate with the working surfaces 49 of the groove 13 are curved so that a cylindrical cross section of the sliding block 44 with flattened end faces 50 is formed (FIG. 2) and a linear contact between the working surfaces 49 and the surfaces also referred to as contact surfaces 51 is guaranteed.

Die in den Figuren 1 bis 3 dargestellte Kraftstoffeinspritzpumpe arbeitet wie folgt: Während mindestens eines Teils des Saughubs des Pumpenkolbens 3 und im Bereich des unteren Totpunktes seiner Hubbewegung strömt aus dem Saugraum 10 über die Schrägnuten 24, die Querbohrung 23 und die Sackbohrung 22 sowie die Saugbohrung 32 Kraftstoff in den Pumpenarbeitsraum 18. Bei dem sich anschließenden, durch Nockenwelle 6, Rolle 5 und Rollenstößel 4 bewirkten Druckhub des Pumpenkolbens 3 baut sich im Pumpenarbeitsraum 18 erst dann der für die Einspritzung erforderliche Druck auf, wenn diese Zuströmkanäle zwischen dem Saugraum 10 und dem Pumpenarbeitsraum 18 gesperrt sind. Solange strömt Kraftstoff wieder aus dem Pumpenarbeitsraum 18 über diese Kanäle zurück in den Saugraum 10. Nach Schließen dieser Kraftstoffsteuerstellen baut sich im Pumpenarbeitsraum 18 der für die Einspritzung erforderliche Hochdruck auf, und es beginnt die Förderung zur Brennkraftmaschine mit der Einspritzung. Nach Zurücklegung des Hochdruckhubes des Pumpenkolbens 3 wird der Pumpenarbeitsraum 18 mit dem Saugraum 10 verbunden, indem die Schrägnuten 24 in Überdeckung mit den Radialbohrungen 25 gelangen, so daß der weitergeförderte Kraftstoff unter hohem Druck abgesteuert wird. Dieser effektive Einspritzhub des Pumpenkolbens 3 hängt von seiner Drehlage ab, die durch die Regelstange 29 bestimmt wird. Je nach Drehlage ist der dadurch bestimmte Abstand der Schrägnuten 24 von den Radialbohrungen 25 unterschiedlich, was einem unterschiedlich langen Einspritzhub entspricht. Die axiale Lage des Steuerschiebers 9 hingegen bestimmt den Beginn der Hochdruckeinspritzung in bezug auf die Drehlage der Nockenwelle 6. Je weiter der Steuerschieber 9 nach oben geschoben ist, desto später tauchen die Schrägnuten 24 in den Steuerschieber 9 ein und desto später, und zwar in exakt gleichem Verhältnis, werden diese Schrägnuten 24 wieder durch die Radialbohrungen 25 zur Beendigung der Einspritzung aufgesteuert. Während die Justierung der einzelnen Steuerschieber 9 für eine entsprechende Zuordnung des Spritzbeginns der einzelnen Pumpenzylinder durch Lageänderung der Verstellbolzen 14 erfolgt, wird die Justierung der Fördermenge der einzelnen Zylinder zueinander dadurch erzielt, daß die Zylinderbüchsen 2 im Pumpengehäuse verdreht werden, so daß durch die Führungsstifte 26 die relative Drehlage der Steuerschieber 9 zu dem Pumpenkolben 3 mit der Folge einer Einspritzmengenkorrektur verstellbar ist. Beim Justieren der Verstellbolzen 14 werden diese in den Querbohrungen 41 der Verdrehwelle 12 so lange verstellt, bis aufgrund der Exzentrizität zwischen Zapfen 37 und Bolzenachse die erforderliche Lage erzielt wird. Bei dieser Justierung liegt der Gleitschuh 44 linienförmig mit seinen Berührungsflächen 51 an den Arbeitsflächen 49 der Quernut 13 des Steuerschiebers 9 an. Aufgrund der Verdrehbarkeit des Gleitschuhs 44 auf dem Zapfen 37 bleibt die Passung zwischen Gleitschuh 44 und Quernut 13 unbeeinträchtigt.The fuel injection pump shown in Figures 1 to 3 works as follows: During at least part of the suction stroke of the pump piston 3 and in the area of the bottom dead center of its stroke movement flows out of the suction chamber 10 via the oblique grooves 24, the transverse bore 23 and the blind bore 22 and the suction bore 32 fuel into the pump work chamber 18. In the subsequent pressure stroke of the pump piston 3 caused by camshaft 6, roller 5 and roller tappet 4, the pressure required for the injection builds up in the pump work chamber 18 only when these inflow channels between the suction chamber 10 and the Pump work space 18 are locked. As long as fuel flows back out of the pump work space 18 via these channels back into the suction space 10. After these fuel control points have been closed, the high pressure required for the injection builds up in the pump work space 18 and the delivery to the internal combustion engine begins with the injection. After the high-pressure stroke of the pump piston 3 has been covered, the pump working chamber 18 is connected to the suction chamber 10 by the inclined grooves 24 coming into overlap with the radial bores 25, so that the fuel which is conveyed on is driven off under high pressure. This effective injection stroke of the pump piston 3 depends on its rotational position, which is determined by the control rod 29. Depending on the rotational position, the distance of the oblique grooves 24 from the radial bores 25 determined thereby is different, which corresponds to an injection stroke of different lengths. The axial position of the control slide 9, on the other hand, determines the start of the high-pressure injection with respect to the rotational position of the camshaft 6. The further the control slide 9 is pushed up, the later the oblique grooves 24 dip into the control slide 9 and the later, specifically same ratio, these oblique grooves 24 are opened again by the radial bores 25 to end the injection. While the adjustment of the individual control slide 9 for a corresponding assignment of the start of spraying of the individual pump cylinders takes place by changing the position of the adjusting bolts 14, the adjustment of the delivery rate of the individual cylinders to one another is achieved in that the cylinder liners 2 are rotated in the pump housing, so that the guide pins 26 the relative rotational position of the control slide 9 to the pump piston 3 is adjustable with the result of an injection quantity correction. When adjusting the adjusting bolts 14, these are adjusted in the transverse bores 41 of the rotating shaft 12 until the required position is achieved due to the eccentricity between the pin 37 and the bolt axis. With this adjustment, the sliding shoe 44 lies linearly with its contact surfaces 51 on the working surfaces 49 of the transverse groove 13 of the control slide 9. Due to the rotatability of the slide shoe 44 on the pin 37, the fit between the slide shoe 44 and the transverse groove 13 remains unaffected.

Das zweite, in den Figuren 4 und 5 mit einer strichpunktiert angedeuteten Ausführungsvariante dargestellte Ausführungsbeispiel unterscheidet sich im wesentlichen von dem zuvor beschriebenen ersten Ausführungsbeispiel durch eine geänderte, nur eine begrenzte Verdrehbarkeit zulassende Lagesicherung des Gleitschuhs und durch den anders gestalteten, unverdrehbar mittels eines Befestigungsbügels an der Verdrehwelle montierten Verstellbolzen. Gleiche Teile sind mit gleichen Bezugszeichen, abweichende Teile mit einem um 100 erhöhten Bezugszeichen und neue Teile mit neuen Bezugszeichen versehen.The second embodiment shown in Figures 4 and 5 with a dash-dotted design variant differs essentially from the previously described first embodiment in a changed, only a limited rotatability to secure the position of the shoe and by the differently designed, non-rotatable by means of a mounting bracket on the Twist shaft mounted adjustment bolt. The same parts are provided with the same reference symbols, different parts with a reference symbol increased by 100 and new parts with new reference symbols.

Der Verstellbolzen 114 des zweiten Ausführungsbeispiels trägt, wie der Verstellbolzen 14 des ersten Ausführungsbeispiels, an seinem in die Quernut 13 des Steuerschiebers 9 eingreifenden Endabschnitt den zylindrischen, den Gleitschuh 144 tragenden Zapfen 137. Der Verstellbolzen 114 ist an einem als U-förmiger Bügel gestalteten Befestigungsteil 115 befestigt und z. B. durch Hartlöten unverdrehbar in seiner Lage festgelegt. Zur Lagesicherung gegen axiales Verschieben auf dem Zapfen 137 ist der parallel zu den Berührungsflächen 51 im Gleitschuh 144 angeordnete und durch eine die Längsachse des Zapfens 137 kreuzende Querbohrung 52 im Zapfen 137 hindurchgesteckte Stift 45 vorgesehen. Die Lage des Stiftes 45 ist, wie bereits zu Figur 3 beschrieben, auch hier durch Abwinkeln seiner freien Enden 47 festgelegt. Der Durchmesser der Querbohrung 52 ist nun um ein solches Maß größer gewählt als der Durchmesser des Stiftes 45, daß ein auf wenige Winkelgrade, vorzugsweise +/-5° in beide Drehrichtungen, begrenztes Verdrehspiel des Gleitschuhs 144 möglich ist. Dieses begrenzte Verdrehspiel dient erstens dem Ausgleich von Fluchtungsfehlern und verhindert somit ein Verklemmen und Verkanten der bei der Steuerung der Hubschieberlage beteiligten Bauteile; und zweitens wird verhindert, daß sich der Gleitschuh 144 aus seiner für die Betätigung der Steuerschieber 9 vorgesehenen Einbaulage beim Einführen der Verdrehwelle 12 wegdreht. Damit ist eine sogenannte "blinde Montage" möglich, d. h. die auf den zuvor in ihrer Einbaulage bezüglich der Verdrehwelle 12 eingestellten Verstellbolzen 114 lagegesichert angebrachten Gleitschuhe 144 zentrieren sich bei der Montage selbsttätig in den sie aufnehmenden Quernuten 13 der Steuerschieber 9, und zwar-mit Hilfe ihrer gewölbten Berührungsflächen 51 und dem Umstand, daß sie sich nur um wenige Winkelgrade aus der endgültigen Einbaulage wegdrehen können.The adjusting bolt 114 of the second exemplary embodiment carries, like the adjusting bolt 14 of the first exemplary embodiment, the cylindrical pin 137 carrying the sliding shoe 144 at its end portion engaging in the transverse groove 13 of the control slide 9. The adjusting bolt 114 is on a fastening part designed as a U-shaped bracket 115 attached and z. B. fixed by brazing in its position. To secure the position against axial displacement on the pin 137, the pin 45, which is arranged parallel to the contact surfaces 51 in the slide shoe 144 and is inserted through a transverse bore 52 crossing the longitudinal axis of the pin 137 in the pin 137, is provided. As already described for FIG. 3, the position of the pin 45 is also fixed here by angling its free ends 47. The diameter of the transverse bore 52 is now chosen to be larger than the diameter of the pin 45 in such a way that a twisting play of the sliding block 144 limited to a few angular degrees, preferably +/- 5 ° in both directions of rotation, is possible. This limited backlash serves firstly to compensate for misalignments and thus prevents jamming and jamming of the components involved in the control of the slide position; and secondly, the slide shoe 144 is prevented from turning away from its installation position provided for the actuation of the control slide 9 when the twisting shaft 12 is inserted. A so-called "blind assembly" is possible, ie the slide shoes 144 mounted on the adjustment bolts 114 previously set in their installed position with respect to the rotating shaft 12 center themselves during assembly in the transverse grooves 13 of the control slide 9 receiving them, with the help of her arched celebrity approximately 51 and the fact that they can only turn a few degrees from the final installation position.

Die zuvor erwähnte, außerhalb des Reglergehäuses vorzunehmende Einstellung der für die richtige Hublage der Steuerschieber 9 verantwortlichen Einbaulage der Verstellbolzen 114 wird durch Austausch verschieden starker Zwischenplättchen zwischen zwei einander gegenüberliegenden Flächen an der Verdrehwelle 12 und dem Befestigungsteil 115 eingestellt, ist hier aber nicht Gegenstand der vorliegenden Erfindung.The aforementioned setting, which is to be carried out outside the controller housing, of the installation position of the adjusting bolts 114, which is responsible for the correct stroke position of the control slide 9, is set by exchanging intermediate plates of different thicknesses between two opposing surfaces on the torsion shaft 12 and the fastening part 115, but is not the subject of the present case Invention.

Sollte es sich herausstellen, daß bei beengten Einbauverhältnissen und relativ großen Lageänderungen des Steuerschiebers mit daraus resultierenden entsprechend großen Verdrehwinkeln der Verdrehwelle 12 sich die aus dem Durchmesserunterschied zwischen Querbohrung 52 und Stift 45 ergebende geringe axiale Verschiebbarkeit des Gleitschuhes 144 ungünstig auf die Zumeßgenauigkeit der Kraftstoffeinspritzpumpe auswirkt, dann ist eine strichpunktiert eingezeichnete Ausführungsvariante zur Lagesicherung vorzuziehen. In dieser Ausführungsvariante nimmt der Stift 45 die gleiche Lage ein wie beim ersten Ausführungsbeispiel nach den Figuren 1 bis 3. Der Stift 45 durchquert dabei den Gleitschuh 144 parallel zu dessen Berührungsflächen 51 und tangential zur Wandung der zentralen Bohrung 40 im Gleitschuh 144. In die zylindrische Mantelfläche 43 des Zapfens 137 am Verstellbolzen 114 ist eine gleichgerichtete Quernut 53 eingearbeitet, in die der Stift 45 mit geringem seitlichen, aber etwas vergrößertem Abstand zum Nutgrund 53a eingreift. Dieser Abstand des Stiftes 45 zum Nutgrund 53a ist so bemessen, daß das bereits zuvor beschriebene, auf wenige Winkelgrade begrenzte Verdrehspiel des Gleitschuhs 144 gewährleistet ist. Außer den bereits zum zweiten Ausführungsbeispiel genannten Vorteilen und Wirkungen gestattet diese Lagesicherung des Gleitschuhs 144 eine weitestmögliche Reduzierung des Axialspiels bei gleichzeitig beibehaltenem Verdrehspiel.If it turns out that, in the case of cramped installation conditions and relatively large changes in position of the control slide, with the resulting correspondingly large angles of rotation of the torsion shaft 12, the small axial displaceability of the slide shoe 144 resulting from the difference in diameter between the transverse bore 52 and pin 45 has an unfavorable effect on the metering accuracy of the fuel injection pump, then a dash-dotted design variant for securing the position is preferable. In this embodiment variant, the pin 45 assumes the same position as in the first exemplary embodiment according to FIGS. 1 to 3. The pin 45 traverses the slide shoe 144 parallel to its contact surfaces 51 and tangentially to the wall of the central bore 40 in the slide shoe 144. In the cylindrical one The lateral surface 43 of the pin 137 on the adjusting bolt 114 has a rectified transverse groove 53, into which the pin 45 engages with a slight lateral but somewhat enlarged distance from the groove base 53a. This distance between the pin 45 and the groove base 53a is dimensioned such that the previously described twisting play of the sliding block 144, which is limited to a few angular degrees, is ensured. In addition to the advantages and effects already mentioned for the second exemplary embodiment, this securing of the position of the sliding shoe 144 allows the greatest possible reduction in the axial play while maintaining the torsional play.

Alle in der vorstehenden Beschreibung erwähnten sowie auch die nur allein aus der Zeichnung entnehmbaren Merkmale, insbesondere der Verstellbolzen 14 und 114 mit Gleitschuhen 44 bzw. 144, sind als weitere Ausgestaltungen Bestandteile der Erfindung, auch wenn sie nicht besonders hervorgehoben und insbesondere nicht in den Ansprüchen erwähnt sind.All of the features mentioned in the above description, as well as the features that can only be inferred from the drawing, in particular the adjusting bolts 14 and 114 with sliding shoes 44 and 144, are further embodiments of the invention, even if they are not particularly emphasized and in particular not in the claims are mentioned.

Claims (6)

1. Fuel injection pump for internal combustion engines, comprising at least one pump element whose pump cylinder, designed as a cylinder liner (2), is secured in a corresponding bore of the pump housing (1) and whose pump plunger (3) is driven for a reciprocating working stroke and is rotatable for controlling the fuel, at least one control slide (9) axially displaceable on the pump plunger (3), and a rotary shaft (12) provided for actuating the control slide (9) for the quantity control and/or the start or end of delivery and mounted in the pump housing, to which rotary shaft (12) at least one radially projecting regulating bolt (14) is fixed which can be set with regard to its fitting position and engages into a transverse groove (13) of the associated control slide (9), characterized in that the regulating bolt (14; 114), at its end section engaging into the transverse groove (13), is designed as a cylindrical stud (37; 137), in that a sliding shoe (44; 144), by means of a largely central bore (40) in the sliding shoe (44; 144), is mounted on the cylindrical stud (37; 137), in that the sliding shoe (44; 144), at right angles to the axis of its central bore (40), has a rectangular shape so that line contact prevails between sliding shoe (44; 144) and transverse groove (13) in both regulating directions of the control slide (9), and in that the sliding shoe (44; 144), in a plane lying in the stud axis and at right angles to the axis of the rotary shaft (12), has a cylindrical cross-section with flattened end faces (50) whose crowned contact surfaces (51) are located opposite the working surfaces (49) of the transverse groove (13).
2. Fuel injection pump according to Claim 1, characterized in that the sliding shoe (44; 144) is secured against axial displacement on the stud (37; 137).
3. Fuel injection pump according to Claim 2, whose regulating bolt is designed as an eccentric bolt, characterized in that a pin (45) arranged in the sliding shoe (44) parallel to the contact surfaces (51) of the sliding shoe (44) and tangentially to the wall of the central bore (40) serves as a securing means, which pin (45) engages into an annular groove (46) arranged in the stud (37).
4. Fuel injection pump according to Claim 2, whose regulating bolt is connected to the rotary shaft via a fastening part in such a way as to be fixed in terms of rotation, characterized in that a pin (45) arranged in the sliding shoe (144) parallel to the contact surfaces (51) of the latter and inserted through a transverse bore (52) in the stud (137) of the regulating bolt (114) serves as a securing means to prevent axial displacement, and the diameter of the transverse bore (52) is larger than the diameter of the pin (45) by such a size that rotary play, limited to a few angular degrees (+/-5°) in both directions of rotation, of the sliding shoe (144) is ensured.
5. Fuel injection pump according to Claim 2, whose regulating bolt is connected to the rotary shaft via a fastening part in such a way as to be fixed in terms of rotation, characterized in that a pin (45) arranged in the sliding shoe (144) parallel to the contact surfaces (51) of the latter and tangentially to the wall of the central bore (40) serves as a securing means to prevent axial displacement, which pin (45) engages into a transverse groove (53) which is made in the cylindrical circumferential surface (43) of the stud (137) on the regulating bolt (114) and whose groove root (53a) is at such a distance from the pin (45) that rotary play, limited to a few angular degrees (+/-5°) in both directions of rotation, of the sliding shoe (144) is ensured.
6. Fuel injection pump according to Claim 3, 4 or 5, characterized in that the pin (45) projects beyond the side faces (48) of the sliding shoe (44; 144), is angled there and is thus fixed so as to be prevented from falling out.
EP87901394A 1986-03-24 1987-03-19 Fuel injection pump for internal combustion engines Expired - Lifetime EP0262167B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3610927 1986-03-24
DE3610927 1986-03-24
DE19873707646 DE3707646A1 (en) 1986-03-24 1987-03-10 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3707646 1987-03-10

Publications (2)

Publication Number Publication Date
EP0262167A1 EP0262167A1 (en) 1988-04-06
EP0262167B1 true EP0262167B1 (en) 1990-05-30

Family

ID=25842516

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901394A Expired - Lifetime EP0262167B1 (en) 1986-03-24 1987-03-19 Fuel injection pump for internal combustion engines

Country Status (5)

Country Link
US (1) US4850823A (en)
EP (1) EP0262167B1 (en)
JP (1) JPS63502914A (en)
DE (2) DE3707646A1 (en)
WO (1) WO1987005969A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041656A1 (en) * 1990-12-22 1992-07-02 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3870748D1 (en) * 1987-07-25 1992-06-11 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES.
DE3736091A1 (en) * 1987-10-24 1989-05-03 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
FI93985C (en) * 1991-04-17 1995-06-26 Waertsilae Diesel Int Mounting and coupling arrangements for a fuel injection pump
JP2017173438A (en) * 2016-03-22 2017-09-28 ヤマハ株式会社 Pin assembly for instrument housing
WO2018162096A1 (en) * 2017-03-09 2018-09-13 Tyrolon-Schulnig Gmbh Carrying apparatus and cam control shaft for gripping devices

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0207283A2 (en) * 1985-06-22 1987-01-07 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2564830A (en) * 1945-11-08 1951-08-21 Bendix Aviat Corp Fuel injection apparatus
US2905020A (en) * 1955-02-24 1959-09-22 Kloeckner Humboldt Deutz Ag Device for use in connection with fuel injection pumps for adjusting the delivery thereof
DE1526725C3 (en) * 1966-08-01 1973-10-25 L'orange Kg, 7000 Stuttgart Multi-cylinder fuel injection pump
US3385221A (en) * 1967-03-07 1968-05-28 Caterpillar Tractor Co Multi-plunger engine fuel oil pump
AU563901B2 (en) * 1984-05-08 1987-07-23 Bosch Automotive Systems Corporation Fuel injection pump and method of adjusting the same pump
JPS6114743U (en) * 1984-06-29 1986-01-28 株式会社ボッシュオートモーティブ システム fuel injector
DE3435987A1 (en) * 1984-10-01 1986-04-10 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
JPS61123756A (en) * 1984-11-16 1986-06-11 Diesel Kiki Co Ltd Fuel injection pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0207283A2 (en) * 1985-06-22 1987-01-07 Robert Bosch Gmbh Fuel injection pump for internal-combustion engines

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041656A1 (en) * 1990-12-22 1992-07-02 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

Also Published As

Publication number Publication date
DE3762985D1 (en) 1990-07-05
WO1987005969A1 (en) 1987-10-08
JPS63502914A (en) 1988-10-27
US4850823A (en) 1989-07-25
DE3707646A1 (en) 1987-10-08
EP0262167A1 (en) 1988-04-06

Similar Documents

Publication Publication Date Title
DE3590194C2 (en) Fuel injection pump
DE3540052C2 (en)
DE2142704B2 (en) Fuel injection pump for multi-cylinder internal combustion engines
DE60317853T2 (en) Crankshaft of an internal combustion engine
DE2729807C2 (en) Fuel injection pump with means for adjusting the start of injection for internal combustion engines
EP0265460B1 (en) Fuel injection pump for internal combustion engines
EP0262167B1 (en) Fuel injection pump for internal combustion engines
EP0207283A2 (en) Fuel injection pump for internal-combustion engines
EP0261154B1 (en) Fuel injection pump for internal combustion engines
DE3911160C2 (en) Fuel injection pump for internal combustion engines
EP0301222B1 (en) Fuel injection pump for internal-combustion engines
DE3435987A1 (en) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3724409C2 (en)
DE3041365A1 (en) INJECTION PUMP DELIVERY DEVICE
EP0313865B1 (en) Fuel injection pump for internal combustion engines
EP0261155B1 (en) Fuel injection pump for internal combustion engines
DE2349655A1 (en) SPEED REGULATOR FOR FUEL INJECTION PUMPS
DE3138640C2 (en)
EP0740742B1 (en) Fuel injection pump
EP0597250B1 (en) Fuel injection pump
DE3718535C2 (en)
DE3320981C2 (en)
DE4137073A1 (en) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3428175A1 (en) Fuel injection pump for internal combustion engines
DE4217939A1 (en) Fuel injection pump for internal combustion engines

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

17P Request for examination filed

Effective date: 19870908

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19880729

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 IT

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

Ref document number: 3762985

Country of ref document: DE

Date of ref document: 19900705

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

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

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

Ref country code: FR

Payment date: 19910329

Year of fee payment: 5

ITTA It: last paid annual fee
26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19921130

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: 19930525

Year of fee payment: 7

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

Ref country code: GB

Payment date: 19940309

Year of fee payment: 8

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

Ref country code: DE

Effective date: 19941201

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

Ref country code: GB

Effective date: 19950319

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

Effective date: 19950319

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050319