EP0534993B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0534993B1
EP0534993B1 EP91909403A EP91909403A EP0534993B1 EP 0534993 B1 EP0534993 B1 EP 0534993B1 EP 91909403 A EP91909403 A EP 91909403A EP 91909403 A EP91909403 A EP 91909403A EP 0534993 B1 EP0534993 B1 EP 0534993B1
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EP
European Patent Office
Prior art keywords
fuel injection
ring
injection pump
roller ring
drive shaft
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
EP91909403A
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German (de)
French (fr)
Other versions
EP0534993A1 (en
Inventor
Wolfgang Fehlmann
Wolfgang Braun
Dieter Junger
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
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Publication of EP0534993A1 publication Critical patent/EP0534993A1/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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/121—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged axially to driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24—Fuel-injection apparatus with sensors

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • a fuel injection pump is already known from DE-OS 33 36 871.
  • the encoder part which is stationary in itself, is directly and firmly attached to the roller ring and is located radially opposite the encoder wheel on the drive shaft.
  • the stationary encoder part can be displaced in the circumferential direction on the roller ring and fixed there again.
  • This solution has the disadvantage that the bearing of the roller ring in the housing of the fuel injection pump is subject to play, so that the roller ring can carry out movements in its radial plane if forces act on it when the cam of the cam disc hits the rollers.
  • the bolt represents a one-sided bearing point of the roller ring, so that when the roller ring is acted upon by forces in its circumferential direction, this tilting movement about the bolt articulation is carried out as the pivot point.
  • the pin linkage itself is also subject to play, as is the pin itself to a certain extent when force is applied transversely to the longitudinal extent of the pin the sprayer can give way. When force is applied to the roller ring, its articulation point also executes a movement in the circumferential direction. If the stationary encoder part is now attached to the roller ring, this will also make this movement.
  • the fixed encoder is generally arranged diametrically opposite the point of articulation of the bolt.
  • the movement components of the roller ring are greatest when it moves around the pin. This results in unwanted or incorrect measurement results in that the transmitter part, which is fixed in itself, moves in the circumferential direction along the sensor wheel with each pump piston stroke, and this leads to incorrect adjustments of the start of fuel injection.
  • this error is added or subtracted, so that the measurement result and the resulting start of injection setting have an uncontrolled proportion of errors. If the speed detection required for the quantity calculation is in the relevant area, this angular error has the effect of a speed error, which means that the quantity calculation is also incorrect.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage over that the movement of the roller ring can be switched off by measurement or at least essentially rendered ineffective by means of the carrier ring due to the retroactive forces of the cam drive.
  • the configuration according to claim 2 provides an advantageous arrangement of the coupling part for coupling the carrier ring to the roller ring.
  • the roller ring natural movements can be virtually completely switched off due to the retroactive forces from the cam drive in relation to the measuring position of the fixed transmitter part.
  • FIG. 1 shows a partial section along the axis of the drive shaft of a distributor fuel injection pump with the parts arranged according to the invention
  • FIG. 2 shows a partial section corresponding to the section according to FIG. 1 in a first modified embodiment as a second exemplary embodiment
  • FIG. 3 shows a section according to the section according to FIG. 1 of a second one modified form as a third embodiment
  • Figure 4 is a partial section according to the section of Figure 1 with a fourth embodiment of the invention.
  • FIG. 1 shows a partial section through a distributor fuel injection pump along the axis of its drive shaft 2, which is mounted with slide bearings 3 in the wall of the housing 4 of the distributor injection pump.
  • the housing includes a pump interior 5 inside, which is filled with fuel under pressure. The filling of the interior is achieved with the aid of a feed pump 6 which is driven by the drive shaft via a feather key 7 and is located in the interior of the pump housing.
  • a pump piston 12 is coupled to the end cam disk via a pin 14, which is held on the end face by a spring 15 in contact with the end cam disk 11.
  • the cams 16 of the front cam disc run over rollers 17 which are mounted in a radial orientation in a roller ring 18. This is with its circular outer contour in a corresponding circular cylindrical recess 19 of the pump housing rotatably, wherein it is supported axially via a skirt 20 and the end face of a disc 21 covering the feed pump 6.
  • the central opening 22 of the roller ring serves for the passage of the claws 9 of the drive shaft or the coupling between the drive shaft and the pump piston with the driving piece and claws of the cam disk 11.
  • the roller ring together with the disk 21 encloses a cylindrical space 23. into which the drive shaft 2 protrudes. There, this has a support collar 25, which is delimited from the pair of claws by a closing collar 26. This final collar is larger in diameter than the supporting collar and rests on the end face 27 of the roller ring 18 delimiting the space 23.
  • a transmitter wheel 30 is now shrunk on the support collar adjacent to the collar 26 and is equipped, for example, with teeth 31 on its end circumference.
  • a support ring 33 is rotatable and arranged axially secured between the washer 28 and the encoder wheel, next to the washer to the washer 28.
  • the carrier ring has an axially encompassing the encoder wheel 30 ring wall 34, on which a fixed part 36 of an angle encoder is arranged, the interacts with its active side with the toothing 31 of the transmitter wheel 30 and adjoins it radially aligned opposite it.
  • the stationary transmitter part is connected to an electronic control device (not shown here) via this cable connection 39.
  • the carrier ring also has a radially projecting pin 41, which projects into a groove 42 in the skirt 20 of the roller ring with the least possible play and thus serves to couple the carrier ring to the roller ring.
  • this pin is arranged at an angular distance of 90 ° from the stationary transmitter part 36 and is shown folded into the plane of the drawing in FIG. 1 only for illustrative reasons.
  • roller ring can be rotated by a spray adjuster piston 43 in a known manner.
  • the roller ring is coupled to the injection adjuster piston 43 via a bolt 45 running radially to the drive shaft.
  • the bolt is usually fixed in the roller ring and connected to the injection adjuster piston 43 with a pivotable connection via a sliding block 46.
  • the drive shaft 2 When the fuel injection pump is in operation, the drive shaft 2 is set in rotating motion. At the same time, the feed pump 6 is also started and the pump interior 5 is supplied with fuel which is under pressure dependent on the speed. This fuel also acts on the injection adjuster piston 43 against a return spring (not shown here) and adjusts this piston more with increasing speed. The resulting rotation of the roller ring causes the cam disc to be set in its conveying stroke movement at an ever earlier point in time when it runs onto the rollers 17. In a known manner, the pump piston 12 leads several per revolution of the drive shaft in this distributor injection pump Delivery strokes from the number of fuel injection valves to be supplied per revolution.
  • the cam disk 11 has a plurality of cams which also act simultaneously with the rollers 17 distributed around the circumference of the roller ring.
  • the cam disk When the cam disk is lifted against the force of the spring 15 and the pressure prevailing in the pump work space in front of the pump piston 12, forces are exerted on the rollers and the roller ring, which are also effective in the circumferential direction according to the cam profile.
  • this causes a backward turning moment on the injection adjuster piston, but on the other hand it also causes the roller ring to move within its guide play in the cylindrical recess.
  • the roller ring held on the bolt 45 the play in the radial plane of the roller ring can cause it to tilt around the bolt as the fulcrum. This tilting movement is also superimposed on the playful connection between pin 45 and roller ring or adjusting piston.
  • the roller ring carries out transverse movements in its radial plane within the specified play.
  • the movable part of the angle encoder, the encoder wheel 30, communicates the stationary encoder part 36 via the toothing 31 with the rotation of the drive shaft and the angular distance that a reference mark, the angular position of which is produced in relation to the base cam, requires to overlap with the stationary encoder part come. If the fixed encoder part moves back and forth together with the roller ring as described above, no exact results are obtained. For this reason, the stationary transmitter part 36 is arranged on the carrier ring 33 and this is mounted on the drive shaft and coupled to the roller ring in the manner described.
  • the position of the coupling pin 41 at a distance of 90 ° from the clamping point on the bolt 45, which lies diametrically opposite the stationary transmitter part 36, causes the adjusting component in the circumferential direction on the carrier ring to be negligibly small when the roller ring is tilted.
  • Both the deflection of the roller ring in the area of the pin 45 and its tilting movement about the pin 45 or injection adjuster piston 43 are taken into account.
  • the coupling pin should be arranged and aligned so that it should be arranged and aligned in the direction of the vertical of the bolt 45 on the roller ring axis.
  • the groove must also be designed or arranged accordingly.
  • the pin 141 which corresponds to the pin 41 in FIG. 1, is provided with a spherical head 48 which projects into the groove 42 of the roller ring 18 with play.
  • This has the advantage that the play between the pin 41 and the roller ring 18 can be kept even smaller, since an alignment error compensation is possible with the help of the head 48, particularly when the roller ring 18 is tilted.
  • the carrier ring is fitted between the collar 26 and the encoder wheel 30 with the least possible play and free mobility in the circumferential direction.
  • the arrangement of the carrier ring 33, 233, 333 on the drive shaft 2 has the advantage that the wear on the slide bearings 3 caused by the operation of the pump and the drive shaft tilting caused thereby do not change the distance between the encoder wheel 30 and the encoder part 36, as a result of which the signal strength remains the same over the lifespan.
  • the simultaneous axial assignment allows the width of the encoder wheel 30 to be reduced to a minimum (manufacturing advantages) without the toothing, as a result of drive shaft axial play, coming from the overlap to the active encoder part, which would likewise result in a deterioration in the signal strength.

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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

A fuel injection pump for internal combustion engines has an angular position sensor consisting of a stationary sensor part (36) and a mobile part in the form of a sensor wheel (30). In order to determine with the greatest possible accuracy the time that elapses between the beginning of injection and the time at which the pump piston stroke actually begins and also the engine speed during delivery, the stationary sensor part is arranged on a supporting ring (33) which is coupled with the roller ring (18) by a pin (41). The pin is set at approximately 90° to the pin (45) which actuates the roller ring. The result of the measurement by the angular position sensor is virtually unaffected by self-movements of the roller ring due to forces of reaction during the pump piston stroke.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Eine solche Kraftstoffeinspritzpumpe ist bereits aus der DE-OS 33 36 871 bekannt. Dort ist der an sich ortsfeste Geberteil unmittelbar fest auf den Rollenring befestigt und liegt radial dem Geberrad auf der Antriebswelle gegenüber. Zu Zentrierungszwecken ist der ortsfeste Geberteil in Umfangsrichtung auf dem Rollenring verschiebbar und dort wieder fixierbar. Diese Lösung hat den Nachteil, daß die Lagerung des Rollenringes im Gehäuse der Kraftstoffeinspritzpumpe spielbehaftet ist, so daß der Rollenring in seiner Radialebene Bewegungen ausführen kann, wenn auf ihn, beim Auflaufen der Nocken der Nockenscheibe auf die Rollen, Kräfte wirken. Dadurch, daß der Rollenring über den Bolzen des Spritzverstellers in Umfangsrichtung verstellbar ist, stellt der Bolzen einen einseitigen Lagerpunkt des Rollenringes dar, so daß bei Beaufschlagung des Rollenringes durch Kräfte in seiner Umfangsrichtung dieser Kippbewegungen um die Bolzenanlenkung als Angelpunkt ausführt. Weiterhin ist die Bolzenanlenkung selbst auch noch spielbehaftet, so wie auch der Bolzen selbst in gewissem Maße bei Kraftbeaufschlagung quer zur Längserstreckung des Bolzens über den Spritzversteller nachgeben kann. Bei Kraftbeaufschlagung des Rollenringes führt somit sein Anlenkpunkt zusätzlich eine Bewegung in Umfangsrichtung aus. Ist nun der ortsfeste Geberteil auf dem Rollenring befestigt, so macht dieser diese Bewegung mit. Aus Platz- bzw. Unterbringungsgründen ist der ortsfeste Geber in der Regel diametral dem Anlenkungspunkt des Bolzens gegenüber angeordnet. In diesem Bereich sind die Bewegungskomponenten des Rollenringes bei seiner Bewegung um den Bolzen am größten. Es ergeben sich somit ungewollte bzw. falsche Meßergebnisse dadurch, daß der an sich ortsfeste Geberteil bei jedem Pumpenkolbenhub sich in Umfangsrichtung entlang dem Geberrad bewegt, und dies führt zu falschen Verstellungen des Kraftstoffeinspritzbeginns. Je nach Betriebsverhältnissen addiert sich oder subtrahiert sich dieser Fehler, so daß das Meßergebnis und die resultierende Spritzbeginneinstellung mit einem unkontrollierten Fehleranteil behaftet ist. Liegt für die Mengenberechnung erforderliche Drehzahlerfassung im betreffenden Bereich, wirkt sich dieser Winkelfehler als Drehzahlfehler aus, wodurch auch die Mengenberechnung fehlerhaft ist.The invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1. Such a fuel injection pump is already known from DE-OS 33 36 871. There, the encoder part, which is stationary in itself, is directly and firmly attached to the roller ring and is located radially opposite the encoder wheel on the drive shaft. For centering purposes, the stationary encoder part can be displaced in the circumferential direction on the roller ring and fixed there again. This solution has the disadvantage that the bearing of the roller ring in the housing of the fuel injection pump is subject to play, so that the roller ring can carry out movements in its radial plane if forces act on it when the cam of the cam disc hits the rollers. Characterized in that the roller ring is adjustable in the circumferential direction via the bolt of the injection adjuster, the bolt represents a one-sided bearing point of the roller ring, so that when the roller ring is acted upon by forces in its circumferential direction, this tilting movement about the bolt articulation is carried out as the pivot point. Furthermore, the pin linkage itself is also subject to play, as is the pin itself to a certain extent when force is applied transversely to the longitudinal extent of the pin the sprayer can give way. When force is applied to the roller ring, its articulation point also executes a movement in the circumferential direction. If the stationary encoder part is now attached to the roller ring, this will also make this movement. For reasons of space or accommodation, the fixed encoder is generally arranged diametrically opposite the point of articulation of the bolt. In this area, the movement components of the roller ring are greatest when it moves around the pin. This results in unwanted or incorrect measurement results in that the transmitter part, which is fixed in itself, moves in the circumferential direction along the sensor wheel with each pump piston stroke, and this leads to incorrect adjustments of the start of fuel injection. Depending on the operating conditions, this error is added or subtracted, so that the measurement result and the resulting start of injection setting have an uncontrolled proportion of errors. If the speed detection required for the quantity calculation is in the relevant area, this angular error has the effect of a speed error, which means that the quantity calculation is also incorrect.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit dem kennzeichnenden Merkmalen des Patentanspruchs 1 hat dem gegenüber den Vorteil, daß mit Hilfe des Trägerringes die Bewegung des Rollenringes aufgrund der rückwirkenden Kräfte des Nockenantriebes meßtechnisch ausgeschaltet oder zumindest im wesentlichen unwirksam gemacht werden.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage over that the movement of the roller ring can be switched off by measurement or at least essentially rendered ineffective by means of the carrier ring due to the retroactive forces of the cam drive.

Durch die Ausgestaltung gemäß Anspruch 2 ist eine vorteilhafte Anordnung des Kupplungsteils zum Kuppeln des Trägerringes mit dem Rollenring angegeben. Gemäß der Ausgestaltung nach Anspruch 3 lassen sich die Rollenringeigenbewegungen aufgrund der rückwirkenden Kräfte vom Nockenantrieb her in bezug auf die Meßstellung des ortsfesten Geberteils praktisch völlig ausschalten.The configuration according to claim 2 provides an advantageous arrangement of the coupling part for coupling the carrier ring to the roller ring. According to the embodiment according to claim 3, the roller ring natural movements can be virtually completely switched off due to the retroactive forces from the cam drive in relation to the measuring position of the fixed transmitter part.

Eine einfach aufzufindende und herzustellende, wirkungsvolle Anordnung des Kupplungsteils ist mit der Lehre des Anspruchs 4 gegeben. Durch die Ausgestaltung nach Anspruch 6 - 8 werden vorteilhafte Lagerungsmöglichkeiten des Trägerrings angegeben und dessen Fixierung in bezug auf die Relativbewegung des ortsfesten Geberteils zum Geberrad. Dabei ergibt sich mit der Ausgestaltung nach Anspruch 7 eine besonders vorteilhafte Lösung.An easy to find and manufacture, effective arrangement of the coupling part is given with the teaching of claim 4. The configuration according to claims 6-8 provides advantageous mounting options for the carrier ring and its fixing in relation to the relative movement of the stationary encoder part to the encoder wheel. The embodiment according to claim 7 results in a particularly advantageous solution.

Zeichnungdrawing

Vier Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigt Figur 1 einen Teilschnitt längs der Achse der Antriebswelle einer Verteilerkraftstoffeinspritzpumpe mit den erfindungsgemäß angeordneten Teilen, Figur 2 einen Teilausschnitt entsprechend dem Schnitt nach Figur 1 in einer ersten abgewandelten Ausführungsform als zweites Ausführungsbeispiel, Figur 3 einen Ausschnitt gemäß dem Schnitt nach Figur 1 einer zweiten abgewandelten Form als drittes Ausführungsbeispiel und Figur 4 einen Teilschnitt gemäß dem Schnitt nach Figur 1 mit einem vierten Ausführungsbeispiel der Erfindung.Four embodiments of the invention are shown in the drawing and are explained in more detail in the following description. 1 shows a partial section along the axis of the drive shaft of a distributor fuel injection pump with the parts arranged according to the invention, FIG. 2 shows a partial section corresponding to the section according to FIG. 1 in a first modified embodiment as a second exemplary embodiment, FIG. 3 shows a section according to the section according to FIG. 1 of a second one modified form as a third embodiment and Figure 4 is a partial section according to the section of Figure 1 with a fourth embodiment of the invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Figur 1 zeigt einen Teilschnitt durch eine Verteilerkraftstoffeinspritzpumpe längs der Achse ihrer Antriebswelle 2, die mit Gleitlagern 3 in der Wand des Gehäuses 4 der Verteilereinspritzpumpe gelagert ist. Das Gehäuse schließt im Innern einen Pumpeninnenraum 5 ein, der mit unter Druck stehendem Kraftstoff gefüllt ist. Die Füllung des Innenraums wird mit Hilfe einer Förderpumpe 6 erzielt, die über eine Paßfeder 7 von der Antriebswelle angetrieben ist und sich im Innern des Pumpengehäuses befindet.FIG. 1 shows a partial section through a distributor fuel injection pump along the axis of its drive shaft 2, which is mounted with slide bearings 3 in the wall of the housing 4 of the distributor injection pump. The housing includes a pump interior 5 inside, which is filled with fuel under pressure. The filling of the interior is achieved with the aid of a feed pump 6 which is driven by the drive shaft via a feather key 7 and is located in the interior of the pump housing.

Am Ende der Antriebswelle befindet sich stirnseitig ein Klauenpaar 9, das über ein Mitnahmestück 10 und entsprechende, nicht gezeigte Klauen eine Stirnnockenscheibe 11 rotierend antreibt. Mit der Stirnnockenscheibe ist bekannterweise ein Pumpenkolben 12 über einen Stift 14 gekoppelt, der durch eine Feder 15 stirnseitig in Anlage an der Stirnnockenscheibe 11 gehalten wird. Die Nocken 16 der Stirnnockenscheibe laufen über Rollen 17, die in radialer Ausrichtung in einem Rollenring 18 gelagert sind. Dieser ist mit seiner kreisförmigen Außenkontur in einer entsprechenden kreiszylindrischen Ausnehmung 19 des Pumpengehäuses drehbar gelagert, wobei er sich axial über eine Schürze 20 und deren Stirnseite an einer die Förderpumpe 6 abdeckenden Scheibe 21 abstützt. Der mittlere Durchbruch 22 des Rollenrings dient zur Durchführung der Klauen 9 der Antriebswelle bzw. Aufnahme der Kupplung zwischen Antriebswelle und Pumpenkolben mit Mitnahmestück und Klauen der Nockenscheibe 11. Im Bereich der Schürze 20 schließt der Rollenring zusammen mit der Scheibe 21 einen zylindrischen Raum 23 ein, in den die Antriebswelle 2 hineinragt. Diese weist dort einen Tragbund 25 auf, der gegenüber dem Klauenpaar durch einen abschließenden Bund 26 abgegrenzt ist. Dieser abschließende Bund ist im Durchmesser größer als der Tragbund und liegt an der den Raum 23 begrenzenden Stirnseite 27 des Rollenrings 18 an. Zwischen Scheibe 21 und Tragbund 25 ist ferner eine Zwischenscheibe 28 gelegt, die den Tragbund antriebswellenseitig abschließt. In dem Raum zwischen Zwischenscheibe 28 und Bund 26 ist nun auf dem Tragbund angrenzend an den Bund 26 ein Geberrad 30 aufgeschrumpft, das an seinem stirnseitigen Umfang beispielsweise mit einer Verzahnung 31 ausgestattet ist. Dem Geberrad nebengeordnet zur Zwischenscheibe 28 hin ist ein Trägerring 33 drehbar und zwischen Zwischenscheibe 28 und Geberrad axial gesichert gelagert. Der Trägerring weist eine axial das Geberrad 30 umfassende Ringwand 34 auf, an der ein ortsfester Teil 36 eines Drehwinkelgebers angeordnet ist, der mit seiner aktiven Seite mit der Verzahnung 31 des Geberrades 30 zusammenwirkt und diesem gegenüberliegend radial ausgerichtet angrenzt. Der ortsfeste Geberteil ist mit einer hier nicht dargestellten elektronischen Steuereinrichtung über diesen Kabelanschluß 39 verbunden.At the end of the drive shaft there is a pair of claws 9 on the end face, which rotates a front cam disk 11 via a driving piece 10 and corresponding claws, not shown. As is known, a pump piston 12 is coupled to the end cam disk via a pin 14, which is held on the end face by a spring 15 in contact with the end cam disk 11. The cams 16 of the front cam disc run over rollers 17 which are mounted in a radial orientation in a roller ring 18. This is with its circular outer contour in a corresponding circular cylindrical recess 19 of the pump housing rotatably, wherein it is supported axially via a skirt 20 and the end face of a disc 21 covering the feed pump 6. The central opening 22 of the roller ring serves for the passage of the claws 9 of the drive shaft or the coupling between the drive shaft and the pump piston with the driving piece and claws of the cam disk 11. In the area of the apron 20, the roller ring together with the disk 21 encloses a cylindrical space 23. into which the drive shaft 2 protrudes. There, this has a support collar 25, which is delimited from the pair of claws by a closing collar 26. This final collar is larger in diameter than the supporting collar and rests on the end face 27 of the roller ring 18 delimiting the space 23. Between washer 21 and support collar 25 there is also an intermediate washer 28 which closes the support collar on the drive shaft side. In the space between the intermediate disk 28 and the collar 26, a transmitter wheel 30 is now shrunk on the support collar adjacent to the collar 26 and is equipped, for example, with teeth 31 on its end circumference. A support ring 33 is rotatable and arranged axially secured between the washer 28 and the encoder wheel, next to the washer to the washer 28. The carrier ring has an axially encompassing the encoder wheel 30 ring wall 34, on which a fixed part 36 of an angle encoder is arranged, the interacts with its active side with the toothing 31 of the transmitter wheel 30 and adjoins it radially aligned opposite it. The stationary transmitter part is connected to an electronic control device (not shown here) via this cable connection 39.

Der Trägerring weist ferner einen radial überstehenden Stift 41 auf, der in eine Nut 42 in der Schürze 20 des Rollenrings hineinragt unter geringst möglichem Spiel und somit der Kupplung des Trägerrings mit dem Rollenring dient. Dabei ist dieser Stift im Winkelabstand von 90° vom ortsfesten Geberteil 36 entfernt angeordnet und lediglich aus darstellerischen Gründen in der Figur 1 in die Zeichnungsebene hineingeklappt gezeichnet.The carrier ring also has a radially projecting pin 41, which projects into a groove 42 in the skirt 20 of the roller ring with the least possible play and thus serves to couple the carrier ring to the roller ring. In this case, this pin is arranged at an angular distance of 90 ° from the stationary transmitter part 36 and is shown folded into the plane of the drawing in FIG. 1 only for illustrative reasons.

Der Rollenring schließlich ist durch einen Spritzverstellerkolben 43 in bekannter Weise verdrehbar. Dazu ist der Rollenring über einen radial zur Antriebswelle verlaufenden Bolzen 45 mit dem Spritzverstellerkolben 43 gekoppelt. Der Bolzen ist üblicherweise im Rollenring fixiert und mit einer schwenkbaren Verbindung über einen Gleitstein 46 mit dem Spritzverstellerkolben 43 verbunden.Finally, the roller ring can be rotated by a spray adjuster piston 43 in a known manner. For this purpose, the roller ring is coupled to the injection adjuster piston 43 via a bolt 45 running radially to the drive shaft. The bolt is usually fixed in the roller ring and connected to the injection adjuster piston 43 with a pivotable connection via a sliding block 46.

Im Betrieb der Kraftstoffeinspritzpumpe wird die Antriebswelle 2 in rotierende Bewegung versetzt. Dabei wird zugleich auch die Förderpumpe 6 in Gang gebracht und der Pumpeninnenraum 5 mit unter drehzahlabhängigem Druck stehenden Kraftstoff versorgt. Dieser Kraftstoff wirkt auch auf den Spritzverstellerkolben 43 entgegen einer hier nicht gezeigten Rückstellfeder und verstellt diesen Kolben mit zunehmender Drehzahl mehr. Die daraus resultierende Verdrehung des Rollenringes bewirkt, daß die Nockenscheibe zu einem immer früheren Zeitpunkt beim Auflaufen auf den Rollen 17 in ihre Förderhubbewegung versetzt wird. In bekannter Weise führt der Pumpenkolben 12 bei dieser Verteilereinspritzpumpe pro Umdrehung der Antriebswelle mehrere Förderhübe aus entsprechend der Zahl der pro Umdrehung zu versorgenden Kraftstoffeinspritzventile. Dazu besitzt die Nockenscheibe 11 mehrere Nocken, die auch zugleich mit dem am Umfang des Rollenring verteilten Rollen 17 wirksam werden. Beim Hub der Nockenscheibe entgegen der Kraft der Feder 15 und dem im Pumpenarbeitsraum vor dem Pumpenkolben 12 herrschenden Druck werden Kräfte auf die Rollen und den Rollenring ausgeübt, die entsprechend dem Nockenverlauf auch in Umfangsrichtung wirksam werden. Dies bewirkt zum einen ein rückdrehendes Moment auf den Spritzverstellerkolben, zum anderen aber auch eine Eigenbewegung des Rollenringes innerhalb seines Führungsspieles in der zylindrischen Ausnehmung. Denkt man sich den Rollenring jedoch am Bolzen 45 festgehalten, so kann durch das Spiel in der Radialebene des Rollenrings dieser um den Bolzen als Drehpunkt kippen. Dieser Kippbewegung überlagert ist zudem auch die spielbehaftete Verbindung zwischen Bolzen 45 und Rollenring bzw. Verstellkolben. Somit führt bei jedem Förderhub des Pumpenkolbens der Rollenring Querbewegungen in seiner Radialebene im Rahmen des angegebenen Spieles aus.When the fuel injection pump is in operation, the drive shaft 2 is set in rotating motion. At the same time, the feed pump 6 is also started and the pump interior 5 is supplied with fuel which is under pressure dependent on the speed. This fuel also acts on the injection adjuster piston 43 against a return spring (not shown here) and adjusts this piston more with increasing speed. The resulting rotation of the roller ring causes the cam disc to be set in its conveying stroke movement at an ever earlier point in time when it runs onto the rollers 17. In a known manner, the pump piston 12 leads several per revolution of the drive shaft in this distributor injection pump Delivery strokes from the number of fuel injection valves to be supplied per revolution. For this purpose, the cam disk 11 has a plurality of cams which also act simultaneously with the rollers 17 distributed around the circumference of the roller ring. When the cam disk is lifted against the force of the spring 15 and the pressure prevailing in the pump work space in front of the pump piston 12, forces are exerted on the rollers and the roller ring, which are also effective in the circumferential direction according to the cam profile. On the one hand, this causes a backward turning moment on the injection adjuster piston, but on the other hand it also causes the roller ring to move within its guide play in the cylindrical recess. However, if you think of the roller ring held on the bolt 45, the play in the radial plane of the roller ring can cause it to tilt around the bolt as the fulcrum. This tilting movement is also superimposed on the playful connection between pin 45 and roller ring or adjusting piston. Thus, with each delivery stroke of the pump piston, the roller ring carries out transverse movements in its radial plane within the specified play.

Dies ist bei üblichen Pumpen an sich kein Problem. Problematisch wird dies aber dann, wenn der Rollenring als an sich ortsfeste Teil eines Winkelgebers die Drehstellung eines beweglichen Teils des Winkelgebers bestimmen soll. Die vom Spritzversteller vorgenommene Verdrehung zur Verstellung des Spritzbeginns soll einer elektrischen Steuereinrichtung rückgemeldet werden, und zwar in bezug auf eine gedachte Drehstellung der Antriebswelle, die synchron zu den Nocken der Nockenscheibe umläuft. So gesehen soll festgestellt werden, zu welchen Punkten der Nockenhubkurve bezogen auf die synchron zur Drehzahl der Brennkraftmaschine angetriebene Antriebswelle die Einspritzung erfolgt. Zusätzlich soll die für die Mengenberechnung notwendige Momentandrehzahl ermittelt werden, welche, wenn sie zeitlich mit dem "Kippen" zusammenfällt, einen Mengenfehler verursachen kann.This is not a problem in itself with conventional pumps. This becomes problematic, however, when the roller ring, as a fixed part of an angle encoder, is intended to determine the rotational position of a movable part of the angle encoder. The rotation made by the injection adjuster to adjust the start of injection should be reported back to an electrical control device, specifically with respect to an imaginary rotational position of the drive shaft, which rotates synchronously with the cams of the cam disk. Seen in this way, it should be determined at which points of the cam lift curve, based on the drive shaft driven synchronously with the speed of the internal combustion engine, the injection takes place. In addition, the instantaneous speed necessary for the quantity calculation should be determined, which, if it coincides with the "tipping", can cause a quantity error.

Der bewegliche Teil des Winkelgebers, das Geberrad 30 teilt dabei den ortsfesten Geberteil 36 über die Verzahnung 31 die Drehung der Antriebswelle mit und den Drehwinkelabstand, den eine Referenzmarke, deren Drehwinkellage zum Basisnocken definiert hergestellt wird, benötigt, um in Überdeckung mit dem ortsfesten Geberteil zu kommen. Bewegt sich nun der ortsfeste Geberteil wie oben beschrieben zusammen mit dem Rollenring hin und her, so ergeben sich keine exakten Ergebnisse. Aus diesem Grunde ist der ortsfeste Geberteil 36 auf den Trägerring 33 angeordnet und dieser auf der Antriebswelle gelagert und auf die beschriebene Art und Weise mit dem Rollenring gekoppelt. Die Lage des koppelnden Stiftes 41 in 90° Abstand vom Einspannpunkt am Bolzen 45, der den ortsfesten Geberteil 36 diametral gegenüberliegt, bewirkt, daß bei einer Kippbewegung des Rollenringes innerhalb der Radialebene die Verstellkomponente in Umfangsrichtung auf den Trägerring vernachlässigbar klein wird. Dabei ist sowohl das Ausweichen des Rollenringes im Bereich des Bolzens 45 als auch seine Kippbewegung um den Bolzen 45 bzw. Spritzverstellerkolben 43 berücksichtigt. Grundsätzlich ist es so, daß der kuppelnde Stift so angeordnet und ausgerichtet sein soll, daß er in Richtung der lotrechten des Bolzens 45 auf der Rollenringachse angeordnet und ausgerichtet sein soll. Entsprechend muß auch die Nut ausgebildet bzw. angeordnet sein.The movable part of the angle encoder, the encoder wheel 30, communicates the stationary encoder part 36 via the toothing 31 with the rotation of the drive shaft and the angular distance that a reference mark, the angular position of which is produced in relation to the base cam, requires to overlap with the stationary encoder part come. If the fixed encoder part moves back and forth together with the roller ring as described above, no exact results are obtained. For this reason, the stationary transmitter part 36 is arranged on the carrier ring 33 and this is mounted on the drive shaft and coupled to the roller ring in the manner described. The position of the coupling pin 41 at a distance of 90 ° from the clamping point on the bolt 45, which lies diametrically opposite the stationary transmitter part 36, causes the adjusting component in the circumferential direction on the carrier ring to be negligibly small when the roller ring is tilted. Both the deflection of the roller ring in the area of the pin 45 and its tilting movement about the pin 45 or injection adjuster piston 43 are taken into account. Basically, it is so that the coupling pin should be arranged and aligned so that it should be arranged and aligned in the direction of the vertical of the bolt 45 on the roller ring axis. The groove must also be designed or arranged accordingly.

In einer Variante zum Ausführungsbeispiel nach Figur 1 ist gemäß Figur 2 der Stift 141, der den Stift 41 in Figur 1 entspricht, mit einem kugelförmigen Kopf 48 versehen, der mit Bewegungsspiel in die Nut 42 des Rollenringes 18 ragt. Dies hat den Vorteil, daß das Spiel zwischen Stift 41 und Rollenring 18 noch geringer gehalten werden kann, da ein Fluchtungsfehlerausgleich insbesondere bei Kippbewegungen des Rollenringes 18 mit Hilfe des Kopfes 48 möglich ist.In a variant of the exemplary embodiment according to FIG. 1, according to FIG. 2, the pin 141, which corresponds to the pin 41 in FIG. 1, is provided with a spherical head 48 which projects into the groove 42 of the roller ring 18 with play. This has the advantage that the play between the pin 41 and the roller ring 18 can be kept even smaller, since an alignment error compensation is possible with the help of the head 48, particularly when the roller ring 18 is tilted.

Um den Trägerring 233 meßgenauer axial zu führen, ist im Ausführungsbeispiel nach Figur 3 der Trägerring zwischen dem Bund 26 und dem Geberrad 30 eingepaßt mit geringestmöglichem Spiel und freier Beweglichkeit in Umfangsrichtung.In order to guide the carrier ring 233 more precisely axially, in the exemplary embodiment according to FIG. 3 the carrier ring is fitted between the collar 26 and the encoder wheel 30 with the least possible play and free mobility in the circumferential direction.

Eine noch genauere Führung ist gemäß dem Ausführungsbeispiel nach Figur 4 möglich, wo der Trägerring an der Ringwand 334 radial nach innen vorspringende, das Geberrad 30 umgreifende Teile 50 aufweist, die an der dem Trägerring 333 abgewandten Stirnseite 51 des Geberrades zur Anlage kommen. Solche übergreifenden Teile 50 sind mehrfach am Umfang des Trägerringes 333 verteilt angeordnet derart, daß das Geberrad 30 noch einsteckbar ist und dann zusammen mit dem Trägerring auf den Tragbund 25 aufgeschrumpft werden kann. Bei dieser Lösung ist eine exakte Zuordnung des ortsfesten Geberteils 36 in Achsrichtung zum Geberrad 30 gewährleistet, so daß ein sehr gleichmäßiges Gebersignal erzeugt werden kann und auch Fehlereinflüsse aus einem axialen Versatz vermieden werden.An even more precise guidance is possible according to the exemplary embodiment according to FIG. 4, where the carrier ring on the ring wall 334 has radially inwardly projecting parts 50 encompassing the sensor wheel 30, which come to rest on the end face 51 of the sensor wheel facing away from the carrier ring 333. Such overlapping parts 50 are distributed several times around the circumference of the carrier ring 333 in such a way that the encoder wheel 30 can still be inserted and can then be shrunk onto the supporting collar 25 together with the carrier ring. In this solution, an exact assignment of the fixed encoder part 36 in the axial direction to the encoder wheel 30 is ensured, so that a very uniform encoder signal can be generated and error influences from an axial offset are avoided.

Die Anordnung des Trägerrings 33, 233, 333 auf der Antriebswelle 2 hat den Vorteil, daß der durch den Betrieb der Pumpe auftretende Verschleiß an den Gleitlagern 3 und das dadurch verursachte Antriebswellenkippen, den Abstand zwischen Geberrad 30 und Geberteil 36 nicht verändert, wodurch die Signalstärke über der Lebensdauer gleichbleibt.The arrangement of the carrier ring 33, 233, 333 on the drive shaft 2 has the advantage that the wear on the slide bearings 3 caused by the operation of the pump and the drive shaft tilting caused thereby do not change the distance between the encoder wheel 30 and the encoder part 36, as a result of which the signal strength remains the same over the lifespan.

Die gleichzeitige axiale Zuordnung erlaubt es, die Breite des Geberrads 30 auf ein Minimum zu reduzieren (Fertigungsvorteile), ohne daß die Verzahnung, infolge Antriebswellenaxialspiels, aus der Überdeckung zum aktiven Geberteil kommen kann, welches ebenfalls eine Verschlechterung der Signalstärke zur Folge hätte.The simultaneous axial assignment allows the width of the encoder wheel 30 to be reduced to a minimum (manufacturing advantages) without the toothing, as a result of drive shaft axial play, coming from the overlap to the active encoder part, which would likewise result in a deterioration in the signal strength.

Claims (8)

  1. Fuel injection pump with a drive shaft which is supported in a wall of the housing (4) of the fuel injection pump and projects into an internal space (5) of the fuel injection pump, where it has an end coupling (9, 10) by which it is coupled to a face cam disc (11) which imparts to a pump plunger (12) a reciprocating and, at the same time, rotary motion, this being achieved by virtue of the fact that the cam disc runs, under the action of a return spring (15) on rollers (17) of a roller ring (18) rotatably mounted in the housing, it being possible to alter the angular position of the roller ring (18) by means of a stud (45) and an injection adjuster (43), connected to the latter, in order to adjust the beginning of injection, and with a sensor wheel (30) which is secured on the drive shaft (2) as the moving part of an angular position sensor and radially opposite which is arranged an essentially fixed part (36) of the angular position sensor, which part can be adjusted together with the roller ring, characterized in that a supporting ring (33, 233, 333) is rotatably mounted on the drive shaft (2) at a location axially adjoining the sensor wheel (30), this supporting ring having a part (34, 334) which overlaps the sensor wheel axially and on which the fixed part (36) is arranged, and the supporting ring is coupled to the roller ring (18) via a coupling part (41, 141) which engages in a cutout (42) in the said roller ring (18).
  2. Fuel injection pump according to Claim 1, characterized in that the coupling part is arranged in the region between the stud (45) engaging on the roller ring (18) and the fixed sensor part (36) situated opposite these.
  3. Fuel injection pump according to Claim 1 or 2, characterized in that the coupling part (41, 141) has a path of motion determined by the radial guide surfaces of the cutout (42).
  4. Fuel injection pump according to Claim 2, characterized in that the coupling part (41, 141) is a pin which projects radially from the supporting ring (33, 233, 333) at an angular spacing of about 90° from the stud (45) and engages in a radially oriented slot (42) in the roller ring (18).
  5. Fuel injection pump according to Claim 4, characterized in that the pin (141) has a head (48) with spherical surfaces which engages in the slot (42).
  6. Fuel injection pump according to one of preceding Claims 1 to 5, characterized in that the drive shaft (2) has a supporting collar (25) which is bounded in the direction of the coupling on the face cam disc side by a collar (26) and on which the sensor wheel (30) is mounted in radially and axially secured fashion, and the support- ing ring (33) is guided, in a manner which allows it to be turned, between the sensor wheel (30) and a part which runs up against the collar (25) on the drive-shaft side (Figure 1).
  7. Fuel injection pump according to Claim 6, characterized in that the supporting ring (333) has parts (50) which reach around the sensor wheel and come to rest against the latter on the side (51) facing away from the supporting ring (Figure 4).
  8. Fuel injection pump according to one of preceding Claims 1 to 5, characterized in that the drive shaft (2) has a supporting collar (25) which is bounded in the direction of the coupling on the face cam disc side by a collar (26) and on which the sensor wheel (30) is mounted in radially and axially secured fashion, and the supporting ring (233) is guided rotatably between the collar (26) and the sensor ring (30) (Figure 3).
EP91909403A 1990-06-20 1991-05-25 Fuel injection pump for internal combustion engines Expired - Lifetime EP0534993B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4019642 1990-06-20
DE4019642A DE4019642A1 (en) 1990-06-20 1990-06-20 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
PCT/DE1991/000439 WO1991019899A1 (en) 1990-06-20 1991-05-25 Fuel injection pump for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0534993A1 EP0534993A1 (en) 1993-04-07
EP0534993B1 true EP0534993B1 (en) 1994-08-17

Family

ID=6408725

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91909403A Expired - Lifetime EP0534993B1 (en) 1990-06-20 1991-05-25 Fuel injection pump for internal combustion engines

Country Status (7)

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US (1) US5357930A (en)
EP (1) EP0534993B1 (en)
JP (1) JP3166857B2 (en)
KR (1) KR0185734B1 (en)
DE (2) DE4019642A1 (en)
ES (1) ES2057896T3 (en)
WO (1) WO1991019899A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4344865A1 (en) * 1993-12-29 1995-07-06 Bosch Gmbh Robert Fuel injection pump
GB9404253D0 (en) * 1994-03-05 1994-04-20 Lucas Ind Plc Fuel injection pumping apparatus
GB9511996D0 (en) * 1995-06-13 1995-08-09 Lucas Ind Plc Fuel system
US6076968A (en) * 1996-11-26 2000-06-20 The Coca-Cola Company Easy open flexible pouch
DE10124265B4 (en) * 2001-05-18 2015-10-29 Gustav Klauke Gmbh pump

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS555423A (en) * 1978-06-24 1980-01-16 Diesel Kiki Co Ltd Distribution-type electronic-control fuel injection system
JPS59221432A (en) * 1983-05-31 1984-12-13 Toyota Motor Corp Distribution type fuel-injection pump
DE3336871A1 (en) * 1983-10-11 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Fuel injection pump for multi-cylinder internal combustion engines
JPS60116853A (en) * 1983-11-26 1985-06-24 Diesel Kiki Co Ltd Distributor type fuel injection pump
JPS60162267U (en) * 1984-04-05 1985-10-28 株式会社ボッシュオートモーティブ　システム distribution type fuel injection pump
JPS62240465A (en) * 1986-04-10 1987-10-21 Diesel Kiki Co Ltd Fuel injection pump
DE3704578A1 (en) * 1987-02-13 1988-08-25 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
US5000668A (en) * 1988-04-27 1991-03-19 Diesel Kiki Co., Ltd. Distribution-type fuel injection pump
GB9026013D0 (en) * 1990-11-29 1991-01-16 Lucas Ind Plc Fuel pumping apparatus

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JP3166857B2 (en) 2001-05-14
ES2057896T3 (en) 1994-10-16
KR930700767A (en) 1993-03-16
KR0185734B1 (en) 1999-03-20
EP0534993A1 (en) 1993-04-07
US5357930A (en) 1994-10-25
WO1991019899A1 (en) 1991-12-26
DE4019642A1 (en) 1992-01-02
DE59102577D1 (en) 1994-09-22
JPH05507776A (en) 1993-11-04

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