EP0192978A1 - Fuel injection pump for internal-combustion engines - Google Patents

Fuel injection pump for internal-combustion engines Download PDF

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Publication number
EP0192978A1
EP0192978A1 EP86101107A EP86101107A EP0192978A1 EP 0192978 A1 EP0192978 A1 EP 0192978A1 EP 86101107 A EP86101107 A EP 86101107A EP 86101107 A EP86101107 A EP 86101107A EP 0192978 A1 EP0192978 A1 EP 0192978A1
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EP
European Patent Office
Prior art keywords
pump according
rollers
housing
roller ring
distributor piston
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.)
Granted
Application number
EP86101107A
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German (de)
French (fr)
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EP0192978B1 (en
Inventor
Franz Eheim
Werner Dipl.-Ing. Pape
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0192978A1 publication Critical patent/EP0192978A1/en
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Publication of EP0192978B1 publication Critical patent/EP0192978B1/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
    • 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

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 for internal combustion engines according to the preamble of claim 1.
  • Such a pump is known for example from DBP 1 039 309, in which the positive guidance of the lifting disc causes the mutually rigid assignment of the pressure rollers to the interception rollers.
  • the interacting parts would have to be manufactured completely tolerance-free; a requirement that cannot be implemented in practice.
  • the invention is based on the idea of providing the zero play play of the lifting disk only at bottom dead center.
  • the minimum diameter of the rolls is 15 millimeters, which results in so-called undercuts on the intercept cam track and causes the intercepting rollers to lift off.
  • Claim 2 prevents or at least reduces this lifting off.
  • Claim 3 proposes a connection of the two roller bearings, which on the one hand has little play and on the other hand does not lead to pressing of the surfaces sliding on one another even in the case of tangential loads and tilting moments
  • a favorable arrangement of the interception rollers on the mating roller ring takes place with claim 6. If the pump is further developed according to claim 7, one achieves a space-saving installation of the positive drive. With the development according to claim 7, a space-saving arrangement is proposed in the axial direction. The mutual bracing of the pressure rollers and the intercepting rollers is achieved with technically simple means by claim 8. With claim 9, a hard impact of the counter roller ring on both stop bolts is avoided and the noise is thereby reduced
  • Claim 13 shows a technically simple way for the spring-elastic connection of the distributor piston to the lifting disk; a space-saving arrangement of the helical compression spring used for this purpose is achieved with the training according to claim 14.
  • FIG. 1 shows, in sections, an axial section through the pump assembly of a fuel injection pump designed as a distributor injection pump for internal combustion engines in natural size
  • Figure 2 shows an axial section through the counter-roller bearing in natural size
  • Figure 3 is a side view of the counter roller ring in natural size
  • FIG. 4 shows the acceleration diagram of the lifting disk during a stroke of the distributor piston
  • FIG. 5 shows phases 2 to 4 of the acceleration diagram in FIG. 4.
  • An executed as so-called distributor injection pump fuel injection pump for internal combustion engines has a bearing in a housing 10 the drive shaft 11 with two jaws 12 which engage in an Oldham 1 3; two claws 14 of a lifting disk 15 engage in these and transmit the rotary movement of the drive shaft 11 to a distributor piston 17 by means of a cross-loop coupling.
  • An intermediate member 18 has the Wienschle i fenkupplung 16 has two offset by 90 degrees and sliding joints 19, 20, wherein the first sliding link 19 with the distributor piston 17 and the second sliding joint 20 cooperating with the eccentric 15 °.
  • 20 form each Schubgefenk 1 9, a groove in the distributor piston 17 and in the cam plate 15 and an engaging groove in the bulge of the intermediate member 18th
  • the distributor piston 17 has a shoulder collar 21, on which one end section of a spring plate 22 is supported and on the other end section of which a helical compression spring 23 rests, which is supported on a support ring 2 4, the support position of which secures a snap ring 25 which is attached to an inner wall 26 of a recess 27 is clamped.
  • the recess 27 is pot-like and recessed in the end face of the lifting disc 15. The pretension of the helical compression spring 23 holds the distributor piston 17 pressed against the intermediate member 18 of the cross-loop coupling
  • a roller ring 28 which can be partially pivoted about the axis 31 in the housing 10 has an outer ring 29 which is supported on an axial shoulder 30 which is fixed to the housing and an inner ring 32 with four end slots 34, each offset by 90 degrees, into the four non-visible axle bolts, each with a pressure roller 33 are used.
  • a counter roller ring 35 (also FIG. 2) is arranged coaxially with respect to the axis 3 1 and has a retaining ring 36 to which two diametrically opposite webs 37 connect, each web 37 pointing radially outwards and forming a stop surface 38.
  • an axle bolt 40 is fastened with an interception roller 41 with respect to the axis 31 and in the radial direction.
  • the end section of both rails 39 is designed as a spring 42, and in the end edge 43 of the roller ring 28 there are two diametrically opposite grooves 44 recessed, which each form a tongue and groove connection with the springs.
  • the counter-roller ring is coupled with the roller 35 and ring 28 with respect thereto slidably in the stroke direction of the distributor piston 1. 7
  • the lifting disk 15 has a pressure cam track 45 and, opposite, a catch cam track 46, which are angularly offset from one another and are coaxial with respect to the distributor piston 17.
  • the pressure cam 4 5 rolls on the pressure rollers 33, and the collecting cam 4 6 in the same way to the Abfangrollen 4. 1
  • a first and second bushing 48 are diametrically opposite one another and arranged parallel to the axis 31.
  • a pin 49 of the bushing 48 is inserted into a bore 50 of the housing 10 and has an annular shoulder 51 between the annular shoulder 51 and the housing 10 is changeable in the axial direction.
  • a stop pin 5 4 is inserted, which is displaceable against the pressure of a helical compression spring 55 and whose spring travel is limited by a transverse pin 56 of the socket 48.
  • a disk spring assembly 58 is slipped onto a sleeve 57 of the bushing 48 that is tapered in diameter, the spring travel of which protrudes beyond the end face of the sleeve 57.
  • the stop pin 48 has a head 60 which interacts with the stop surface 38 of the counter roller ring 35 and limits the spring travel of the plate spring assembly 58.
  • the forced movement of the lifting disc 15 between the pressure rollers 33 and the intercepting rollers 41, which brings about a rotary stroke of the distributor piston 17, takes place as follows with reference to FIGS. 4 and 5:
  • the lifting disc 15 is supported on the pressure rollers 33 during the acceleration phase 1 (acceleration diagram 62) is lifted off the interception rollers 41.
  • acceleration phase 1 acceleration diagram 62
  • this passes through the deceleration phase 2 before TDC and is supported on the intercepting rollers 41, which pass through the deflection path of the helical compression springs 55 until they strike the plate spring assembly 58.
  • the lifting disc 15 is lifted off the pressure rollers 33.
  • the lifting disc 15 maintains this assignment during the deceleration phase 3 to TDC.
  • the lifting disc 15 lifts off the intercepting rollers 41 and strikes the pressure rollers 33 as a result of the inertial forces.
  • the intercepting rollers 4 1 are pressed against the intercepting cam track 4 6 by the helical compression springs 55.
  • the pressure rollers 33 and the intercepting rollers 41 bear against the cooperating cam tracks 45 and 46 during the passage of the distributor piston 17 in the UT.

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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

1. Fuel injection pump for internal-combustion engines with a distributor piston (17), which executes a rotary stroke in a cylinder of the casing of the pump and feeds fuel to the cylinders of the internal-combustion engine according to its stroke and delivery phases and with a cam plate (15), which can be driven by a shaft (11) and has a pressure cam (45) and an interception cam (46), and with a plurality of pressure rollers (33), which are supported axially on the casing and are mounted in roller ring (28) and of interception rollers (41), which are mounted in a counter-roller ring (35), both roller rings being supported axially on the casing (10), on which rollers the cams roll and thereby bring about a guidance of the cam plate (15) effecting the rotary stroke, characterized in that the force of at least one spring (55) acts on the counter-roller ring (35), by which force the counter-roller ring (35) can be displaced by an amount determined by a stop (57, 58, 60) and defining a play.

Description

Stand der TechnikState of the art

- Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1. Eine derartige Pumpe ist beispielsweise aus der DBP 1 039 309 bekannt, bei der die Zwangslaufführung der Hubscheibe die gegenseitige starre Zuordnung der Druckrollen zu den Abfangrollen bewirkt. Um mit dieser Zuordnung einen funktionierenden Zwangslauf zu erreichen, müßten die zusammenwirkenden Teile völlig toleranzfrei gefertigt sein; ein in der Praxis nicht durchführbare Forderung.- The invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1. Such a pump is known for example from DBP 1 039 309, in which the positive guidance of the lifting disc causes the mutually rigid assignment of the pressure rollers to the interception rollers. In order to achieve a functioning positive run with this assignment, the interacting parts would have to be manufactured completely tolerance-free; a requirement that cannot be implemented in practice.

Vorteile der ErfindungAdvantages of the invention

Mit der Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Erfindung wird das im Stand der Technik dargelegte Problem der Zwangslaufführung mit technisch einfachen Mittel gelöst Der Erfindung liegt der Gedanke zugrunde, die spielfreie Zwangtaufführung der Hubscheibe nur im unteren Totpunkt vorzusehen.With the fuel injection pump for internal combustion engines according to the invention, the problem of forced operation described in the prior art is solved with technically simple means. The invention is based on the idea of providing the zero play play of the lifting disk only at bottom dead center.

Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen beschrieben. Aus schleiftechnischen Gründen ist der Mindestdurchmesser der Rolfen 15 Millimeter, was sogenannte Hinterschneidungen an der Abfangnockenbahn ergibt und ein Abheben der Abfangrollen verursacht Mit Anspruch 2 wird dieses Abheben verhindert oder zumindest verringert. Mit Anspruch 3 wird eine Verbindung der beiden Rollenlager vorgeschlagen, die einerseits spielarm ist und andererseits auch bei Tangentialbelastungen und Kippmomenten zu keinem Pressen der aufeinander gleitenden Flächen führtAdvantageous developments of the invention are described in the subclaims. For grinding reasons, the minimum diameter of the rolls is 15 millimeters, which results in so-called undercuts on the intercept cam track and causes the intercepting rollers to lift off. Claim 2 prevents or at least reduces this lifting off. Claim 3 proposes a connection of the two roller bearings, which on the one hand has little play and on the other hand does not lead to pressing of the surfaces sliding on one another even in the case of tangential loads and tilting moments

Eine günstige Anordnung der Abfangrollen am Gegenrollenring erfolgt mit Anspruch 6. Wird die Pumpe gemäß Anspruch 7 weitergebildet, so erreicht man einen platzsparenden Einbau des Zwangslauftriebwerks. Mit der Weiterbildung nach Anspruch 7 wird eine in axialer Richtung platzsparender Anordnung vorgeschlagen. Die gegenseitige Verspannung der Druckrollen und der Abfangrollen erreicht man mit technisch einfachen Mitteln durch Anspruch 8. Mit Anspruch 9 wird ein hartes Anschlagen des Gegenrollenringes an beiden Anschlagbolzen vermieden und dadurch das Geräusch germindertA favorable arrangement of the interception rollers on the mating roller ring takes place with claim 6. If the pump is further developed according to claim 7, one achieves a space-saving installation of the positive drive. With the development according to claim 7, a space-saving arrangement is proposed in the axial direction. The mutual bracing of the pressure rollers and the intercepting rollers is achieved with technically simple means by claim 8. With claim 9, a hard impact of the counter roller ring on both stop bolts is avoided and the noise is thereby reduced

Mit Anspruch 11 ist das Spiel zwischen den Rollen und der Hubscheibe justierbar. Wird die Kraftstoffeinspritzpumpe gemäß Anspruch 12 mit zwei translatorischen und zwei rotatorischen Freiheitsgraden weitergebildet, so lassen sich sogenannte Kolbenfresser mit Sicherheit vermeiden. Mit Anspruch 13 wird ein technisch einfacher Weg für die federelastische Verbindung des Verteilerkolbens mit der Hubscheibe gewiesen; eine platzsparende Anordnung der hierfür verwendeten Schraubendruckfeder erreicht man mit der Weiterbifdung nach Anspruch 14.With claim 11, the game between the rollers and the lifting disc is adjustable. If the fuel injection pump is developed with two translational and two rotational degrees of freedom, so-called piston seizures can be avoided with certainty. Claim 13 shows a technically simple way for the spring-elastic connection of the distributor piston to the lifting disk; a space-saving arrangement of the helical compression spring used for this purpose is achieved with the training according to claim 14.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der folgenden Figurenbeschreibung näher erläutert. Es zeigen: Figur 1 abschnittsweise einen Achsialschnitt durch den Pumpenverband einer als Verteilereinspritzpumpe ausgeführten Kraftstoffeinspritzpumpe für Brennkraftmaschinen in natürlicher Größe; Figur 2 einen Achsialschnitt durch das Gegenrollenlager in natürlicher Größe; Figur 3 eine Seitenansicht des Gegenrollenringes in natürlicher Größe; und Figur 4 das Beschleunigungsdiagramm der Hubscheibe während eines Hubes des Verteilerkolbens; und Figur 5 die Phasen 2 bis 4 des Beschleunigungsdiagrammes in Figur 4.An embodiment of the invention is shown in the drawing and explained in more detail in the following description of the figures. 1 shows, in sections, an axial section through the pump assembly of a fuel injection pump designed as a distributor injection pump for internal combustion engines in natural size; Figure 2 shows an axial section through the counter-roller bearing in natural size; Figure 3 is a side view of the counter roller ring in natural size; and FIG. 4 shows the acceleration diagram of the lifting disk during a stroke of the distributor piston; and FIG. 5 shows phases 2 to 4 of the acceleration diagram in FIG. 4.

Beschreibung des Ausführungsbeispieles.Description of the embodiment.

Eine als sogenannte Verteilereinspritzpumpe ausgeführte Kraftstoffeinspritzpumpe für Brennkraftmaschinen hat eine in einem Gehäuse 10 gelagerte Antriebswelle 11 mit zwei Klauen 12, die in eine Kreuzscheibe 13 eingreifen; in diese greifen zwei Klauen 14 einer Hubscheibe 15 ein, die durch eine Kreuzschleifenkupplung die Drehbewegung der Antriebswelle 11 auf einen Verteilerkolben 17 übertragen.An executed as so-called distributor injection pump fuel injection pump for internal combustion engines has a bearing in a housing 10 the drive shaft 11 with two jaws 12 which engage in an Oldham 1 3; two claws 14 of a lifting disk 15 engage in these and transmit the rotary movement of the drive shaft 11 to a distributor piston 17 by means of a cross-loop coupling.

Ein Zwischenglied 18 der Kreuzschleifenkupplung 16 hat zwei um 90 Grad versetzte Schubgelenke 19, 20, wobei das erste Schubgelenk 19 mit dem Verteilerkolben 17 und das zweite Schubgelenk 20 mit der Hubscheibe 15 zusammenwirken. Dabei bilden jedes Schubgefenk 19, 20 eine Nut im Verteilerkolben 17 bzw. in der Hubscheibe 15 und ein in die Nut eingreifender Wulst des Zwischengliedes 18.An intermediate member 18 has the Kreuzschle i fenkupplung 16 has two offset by 90 degrees and sliding joints 19, 20, wherein the first sliding link 19 with the distributor piston 17 and the second sliding joint 20 cooperating with the eccentric 15 °. In this case, 20 form each Schubgefenk 1 9, a groove in the distributor piston 17 and in the cam plate 15 and an engaging groove in the bulge of the intermediate member 18th

Der Verteilerkolben 17 hat einen eine Schulter bildenden Ringbund 21, an dem sich der eine Endabschnitt eines Federtellers 22 abstützt und an dessen anderem Endabschnitt eine Schraubendruckfeder 23 anliegt, die sich an einem Stützring 24 abstützt dessen Stützlage sichert ein Sprengring 25, der an einer Innenwandung 26 einer Aussparung 27 festklemmt Die Aussparung 27 ist topfartig und in der Stirnseite der Hubscheibe 15 ausgespart Die Vorspannung der Schraubendruckfeder 23 hält den Verteilerkolben 17 an das Zwischenglied 18 der Kreuzschleifenkupplung gedrücktThe distributor piston 17 has a shoulder collar 21, on which one end section of a spring plate 22 is supported and on the other end section of which a helical compression spring 23 rests, which is supported on a support ring 2 4, the support position of which secures a snap ring 25 which is attached to an inner wall 26 of a recess 27 is clamped. The recess 27 is pot-like and recessed in the end face of the lifting disc 15. The pretension of the helical compression spring 23 holds the distributor piston 17 pressed against the intermediate member 18 of the cross-loop coupling

Ein im Gehäuse 10 um die Achse 31 teilweise - schwenkbarer Rollenring 28 hat einen sich an einer gehäusefesten Axialschulter 30 abstützenden Außenring 29 und einen Innenring 32 mit jeweils vier, um 90 Grad winkelversetzte Stimschlitze 34, in die vier nicht sichtbare Achsbolzen mit jeweils einer Druckrolle 33 eingesetzt sind.A roller ring 28 which can be partially pivoted about the axis 31 in the housing 10 has an outer ring 29 which is supported on an axial shoulder 30 which is fixed to the housing and an inner ring 32 with four end slots 34, each offset by 90 degrees, into the four non-visible axle bolts, each with a pressure roller 33 are used.

Ein Gegenrollenring 35 (auch Figur 2) ist bezüglich der Achse 31 koaxial angeordnet und hat einen Haltering 36, an dem sich zwei einander diametral gegenüberliegende Stege 37 anschließen, wobei jeder Steg 37 radial nach außen weist und eine Anschlagfläche 38 bildet. An jedem Steg 37 setzt sich eine bezüglich des Verteilerkolbens 17 achsparallefe Schiene 39 fort, die an der Innenwandung des Gehäuses 10 geführt istA counter roller ring 35 (also FIG. 2) is arranged coaxially with respect to the axis 3 1 and has a retaining ring 36 to which two diametrically opposite webs 37 connect, each web 37 pointing radially outwards and forming a stop surface 38. On each web 37 there is a rail 39 which is axially parallel to the distributor piston 17 and is guided on the inner wall of the housing 10

Im Haltering 36 und in beiden Schienen 39 ist bezüglich der Achse 31 und in radialer Richtung ein Achsbolzen 40 mit einer Abfangrolle 41 befestigt Der Endabschnitt beider Schienen 39 ist als Feder 42 ausgebildet, und in der Stimkante 43 des Rollenringes 28 sind zwei diametral gegenüberliegende Nuten 44 ausgespart, die mit den Federn jeweils eine Nut-Feder-Verbindung bilden. Hierdurch ist der Gegenrollenring 35 mit dem Rollenring 28 gekuppelt und bezüglich diesem in Hubrichtung des Verteilerkolbens 17 verschiebbar.In the retaining ring 36 and in both rails 39, an axle bolt 40 is fastened with an interception roller 41 with respect to the axis 31 and in the radial direction. The end section of both rails 39 is designed as a spring 42, and in the end edge 43 of the roller ring 28 there are two diametrically opposite grooves 44 recessed, which each form a tongue and groove connection with the springs. In this way, the counter-roller ring is coupled with the roller 35 and ring 28 with respect thereto slidably in the stroke direction of the distributor piston 1. 7

Die Hubscheibe 15 hat eine Drucknockenbahn 45 und gegenüberliegend eine Auffangnockenbahn 46, die gegeneinander winkelversetzt und bezüglich des Verteilerkolbens 17 koaxial sind. Hierbei wälzt sich die Drucknockenbahn 45 auf den Druckrollen 33 ab, und die Auffangnockenbahn 46 in gleicher Weise auf den Abfangrollen 41.The lifting disk 15 has a pressure cam track 45 and, opposite, a catch cam track 46, which are angularly offset from one another and are coaxial with respect to the distributor piston 17. Here, the pressure cam 4 5 rolls on the pressure rollers 33, and the collecting cam 4 6 in the same way to the Abfangrollen 4. 1

Eine erste und zweite Buchse 48 sind einander diametral gegenüberliegend und bezüglich der Achse 31 parallel angeordnet Ein Zapfen 49 der Buchse 48 ist in einer Bohrung 50 des Gehäuses 10 eingesetzt und hat eine Ringschulter 51. Auf den Zapfen 49 sind Ausgleichsscheiben 52 aufsteckbar, wodurch der Abstand zwischen der Ringschulter 51 und dem Gehäuse 10 in axialer Richtung veränderbar ist. In einem konzentrischen Sackloch 53 der Buchse 48 ist ein Anschlagbolzen 54 eingesteckt, der gegen den Druck einer Schraubendruckfeder 55 verschiebbar ist und dessen Federweg durch einen Querstift 56 der Buchse 48 begrenzt wird.A first and second bushing 48 are diametrically opposite one another and arranged parallel to the axis 31. A pin 49 of the bushing 48 is inserted into a bore 50 of the housing 10 and has an annular shoulder 51 between the annular shoulder 51 and the housing 10 is changeable in the axial direction. In a concentric blind hole 53 of the socket 4 8, a stop pin 5 4 is inserted, which is displaceable against the pressure of a helical compression spring 55 and whose spring travel is limited by a transverse pin 56 of the socket 48.

Auf einer stirnseitig, im Durchmesser verjüngten Hülse 57 der Buchse 48 ist ein Tellerfederpaket 58 aufgesteckt, dessen Federweg über die Stirnseite der Hülse 57 hinausragt. Der Anschlagbolzen 48 hat einen Kopf 60, der mit der Anschlagfläche 38 des Gegenrollenringes 35 zusammenwirkt und den Federweg das Tellerfederpaket 58 begrenzt.A disk spring assembly 58 is slipped onto a sleeve 57 of the bushing 48 that is tapered in diameter, the spring travel of which protrudes beyond the end face of the sleeve 57. The stop pin 48 has a head 60 which interacts with the stop surface 38 of the counter roller ring 35 and limits the spring travel of the plate spring assembly 58.

Die Zwanglaufführung der Hubscheibe 15 zwischen den Druckrollen 33 und den Abfangrollen 41, die einen Drehhub des Verteilerkolbens 17 bewirkt, erfolgt anhand der Figuren 4 und 5 folgermaßen: Die Hubscheibe 15 stützt sich während der Beschleunigungsphase 1 (Beschleunigungsdiagramm 62) an den Druckrollen 33 ab und ist von den Abfangrollen 41 abgehoben. Beim Weiterdrehen gemäß Pfeil 61 der Hubscheibe 15 durchläuft diese die Verzögerungsphase 2 vor OT und stützt sich dabei an den Abfangrollen 41 ab, die den Einfederungsweg der Schraubendruckfedern 55 bis zum Anschlagen an das Tellerfederpaket 58 durchlaufen. In dieser Phase ist die Hubscheibe 15 von den Druckrollen 33 abgehoben. Diese Zuordnung behält die Hubscheibe 15 während der Verzögerungsphase 3 bis OT bei. Während der Beschleunigungsphase 4 nach OT hebt die Hubscheibe 15 von den Abfangrollen 41 ab und schlägt infolge der Trägheitskräfte auf den Druckrollen 33 .auf. Spätestens bei Beginn 63 des UT (unterer Totpunkt) sind die Abfangrollen 41 durch die Schraubendruckfedern 55 an die Abfangnockenbahn 46 angedrückt. Mithin liegen die Druckrollen 33 und die Abfangrollen 41 an den zusammenwirkenden Nockenbahnen 45 bzw. 46 während des Durchganges des Verteilerkolbens 17 im UT an.The forced movement of the lifting disc 15 between the pressure rollers 33 and the intercepting rollers 41, which brings about a rotary stroke of the distributor piston 17, takes place as follows with reference to FIGS. 4 and 5: The lifting disc 15 is supported on the pressure rollers 33 during the acceleration phase 1 (acceleration diagram 62) is lifted off the interception rollers 41. When turning further according to arrow 6 1 of the lifting disc 15, this passes through the deceleration phase 2 before TDC and is supported on the intercepting rollers 41, which pass through the deflection path of the helical compression springs 55 until they strike the plate spring assembly 58. In this phase, the lifting disc 15 is lifted off the pressure rollers 33. The lifting disc 15 maintains this assignment during the deceleration phase 3 to TDC. During the acceleration phase 4 after TDC, the lifting disc 15 lifts off the intercepting rollers 41 and strikes the pressure rollers 33 as a result of the inertial forces. At the latest at the beginning 63 of the UT (bottom dead center), the intercepting rollers 4 1 are pressed against the intercepting cam track 4 6 by the helical compression springs 55. Thus, the pressure rollers 33 and the intercepting rollers 41 bear against the cooperating cam tracks 45 and 46 during the passage of the distributor piston 17 in the UT.

Claims (14)

1. Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit einem in einem Zylinder des Gehäuses der Pumpe einen Drehhub ausführenden Verteilerkolben, der entsprechend seinen Hub-und Förderphasen Kraftstoff den Zylindern der Brennkraftmaschine zuführt, und mit einer durch eine Welle antreibbare Hubscheibe, die eine Drucknockenbahn sowie eine Abfangnockenbahn aufweist, und mit mehreren am Gehäuse axial sich abstützenden Druckrollen sowie Abfangrollen, auf denen die Nockenbahnen sich abwälzen und hierdurch eine den Drehhub bewirkende Führung der Hubscheibe herbeiführen, dadurch gekennzeichnet, daß die Hubscheibe (15) während der Beschleunigungs-und Verzögerungsphasen (1-4) des Verteilerkolbens (17)/der Hubscheibe (15) mit Spiel zwischen den Druckrollen (33) und den Abfangrollen (41) geführt ist.1.Fuel injection pump for internal combustion engines with a distributor piston which executes a rotary stroke in a cylinder of the pump housing and which supplies fuel to the cylinders of the internal combustion engine in accordance with its stroke and delivery phases, and with a lifting disk which can be driven by a shaft and which has a pressure cam track and an intercept cam track. and with several pressure rollers axially supported on the housing as well as intercepting rollers on which the cam tracks roll and thereby bring about the guiding of the lifting disc, causing the turning stroke, characterized in that the lifting disc (15) during the acceleration and deceleration phases (1-4) of the Distributor piston (17) / the lifting disc (15) with play between the pressure rollers (33) and the interception rollers (4 1 ) is guided. 2. Pumpe nach Anspruch 1 mit einem die Druckrollen (33) aufnehmenden Rollenring (28) und mit einem die Abfangroilen (41) aufnehmenden Gegenrollenring (35), wobei beide Rollenringe sich am Gehäuse (10) axial abstützen, dadurch gekennzeichnet, daß auf den Gegenrollenring (35) die Kraft einer Feder (55) derart einwirkt, daß die Abfangrollen (41) während beider Verzögerungsphasen (2 und 3) -mindestens jedoch vor OT (oberer Totpunkt)-an der Abfangnockenbahn (46) anliegen.2. Pump according to claim 1 with a pressure roller (33) receiving roller ring (28) and with a catch rollers (41) receiving counter roller ring (35), both roller rings being axially supported on the housing (10), characterized in that on the Counter roller ring (35) acts on the force of a spring (55) such that the interception rollers ( 41 ) bear against the interception cam track (46) during both deceleration phases (2 and 3) - at least before TDC (top dead center). 3. Pumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Rollenring (28) mit den Druckrollen (33) und der Gegenrollenring (35) mit den Abfangrollen (41) durch eine Nut-Feder-Verbindung (42/44) in Hubrichtung des Verteilerkolbens (17) miteinander gekuppelt sind.3. Pump according to claim 1 or 2, characterized in that the roller ring (28) with the pressure rollers (33) and the counter roller ring (35) with the intercepting rollers (41) by a tongue and groove connection (42/44) in the stroke direction of the distributor piston (17) are coupled together. 4. Pumpe nach Anspruch 3, dadurch gekennzeichnet, daß der Gegenrollenring (35) mindestens zwei bezüglich des Verteilerkolbens (17) achsparallele Schienen (39) aufweist, die an der Innenwandung des Gehäuses (10) geführt sind, und daß der Rollenring (28) und die Schiene (39) die Nut-Feder-Verbindung (42/44) bilden.4. Pump according to claim 3, characterized in that the counter roller ring (35) has at least two axially parallel rails (39) with respect to the distributor piston (17) which are guided on the inner wall of the housing (10), and in that the roller ring (28) and the rail (39) form the tongue and groove connection (42/44). 5. Pumpe nach Anspruch 4, dadurch gekennzeichnet, daß der Endabschnitt der Schiene (35) als Feder (42) ausgebildet ist und daß die Stirnkante (43) des Rollenringes (28) beide Nuten (44) aufweist. 5 . Pump according to Claim 4, characterized in that the end section of the rail (35) is designed as a spring (42) and in that the end edge (43) of the roller ring (28) has both grooves (44). 6. Pumpe nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß die Schiene (39) über einen Steg (37) an einem Haltering (36) angeformt ist und daß in der Schiene (39) und im Haltering (36) die Abfangrolle (41) befestigt ist.6. Pump according to claim 4 or 5, characterized in that the rail (39) via a web (37) on a retaining ring (36) is integrally formed and that in the rail (39) and in the retaining ring (36), the interception roller (41 ) is attached. 7. Pumpe nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, daß die Drucknockenbahn (45) und die Auffangnockenbahn (46) gegeneinander winkelversetzt und bezüglich des Verteilerkolbens (17) koaxial angeordnet sind.7. Pump according to one of the preceding claims, characterized in that the pressure cam track ( 4 5) and the collecting cam track (46) are angularly offset from one another and are arranged coaxially with respect to the distributor piston (17). 8. Pumpe nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß der Steg (37) der Schiene (39) als Anschlagfläche (38) ausgebildet ist, die mit einem am Gehäuse (10) abgestützten Anschlagbolzen (54) zusammenwirkt, und daß die das Anliegen der Abfangrollen (41) an der Abfangnockenbahn (46) bewirkende Federkraft eine Druckfeder -insbesondere eine Schraubendruckfeder (55) -bewirkt, die zwischen dem Anschlagbolzen (54) und dem Gehäuse (10) angeordnet ist.8. Pump according to claim 6 or 7, characterized in that the web (37) of the rail (39) is designed as a stop surface (38) which cooperates with a stop bolt (54) supported on the housing (10), and that the If the intercepting rollers (41) bear against the interlocking cam track (46), a compression spring - in particular a helical compression spring (55) - is arranged, which is arranged between the stop bolt (54) and the housing (10). 9. Pumpe nach Anspruch 8, dadurch gekennzeichnet, daß am Gehäuse (10) eine Buchse (48) mit einem die Schraubendruckfeder (55) aufnehmenden Sackloch (53) festgelegt ist.9. Pump according to claim 8, characterized in that on the housing (10) a socket (48) with a helical compression spring (55) receiving blind hole (53) is fixed. 10. Pumpe nach Anspruch 9, dadurch gekennzeichnet, daß der Anschlagbolzen (54) einen Kopf (60) aufweist, daß die Buchse (48) eine im Durchmesser verjüngte Hülse (57) hat, auf der eine Druckfeder -insbesondere ein Tellerfederpaket (58) -aufgesteckt ist, dessen Federweg über die Stirnseite in der Hülse (57) hinausragt. 1 0. Pump according to claim 9, characterized in that the stop pin (54) has a head (60), that the bushing (48) has a tapered sleeve (57) on which a compression spring - in particular a plate spring assembly (58 ) is attached, the spring travel of which projects beyond the end face in the sleeve (57). 11. Pumpe nach Anspruch 8 oder 9, dadurch gekennzeichnet, daß die Buchse (48) einen in einer Bohrung (50) des Gehäuses (10) eingesetzten Zapfen (49) und eine Ringschulter (51) aufweist und daß durch auf den Zapfen (49) aufgesteckte Ausgleichsscheiben (52) der Abstand zwischen der Ringschulter (51) und dem Gehäuse (10) veränderbar ist.1 1 . Pump according to Claim 8 or 9, characterized in that the bushing (48) has a pin ( 4 9) inserted in a bore (50) of the housing (10) and an annular shoulder (51) and in that the pin (49) fitted shims (52) the distance between the annular shoulder (5 1 ) and the housing ( 1 0) can be changed. 12. Pumpe nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, daß der Verteilerkolben (17) und die Hubscheibe (15) durch eine Kreuzschleifenkupplung verbunden sind, deren Zwischenglied (18) zwei um 90 Grad versetzte Schubgelenke (19, 20) aufweist, wobei das eine Schubgelenk (19) mit dem Verteilerkolben (17) und das andere Schubgelenk (20) mit der Hubscheibe (15) zusammenwirken.12. Pump according to one of the preceding claims, characterized in that the distributor piston (17) and the lifting disc (15) are connected by a cross-loop coupling, the intermediate member (18) having two thrust joints (19, 20) offset by 90 degrees, the a Interact thrust joint ( 1 9) with the distributor piston (17) and the other thrust joint (20) with the lifting disc (15). 13. Pumpe nach Anspruch 12, dadurch gekennzeichnet, daß eine Druckfeder -insbesondere eine Schraubendruckfeder (23) -den Verteilerkolben (17) an das Zwischenglied - (18) der Kreuzschleifenkupplung (16) gedrückt hält13. Pump according to claim 12, characterized in that a compression spring, in particular a helical compression spring (23), holds the distributor piston ( 1 7) to the intermediate member (18) of the cross-loop coupling (16) 14. Pumpe nach Anspruch 13, dadurch gekennzeichnet, daß die Stirnseite der Hubscheibe (15) eine topfartige Aussparung (27) aufweist und daß die Schraubendruckfeder - (23) sich zum einen an der Innenwandung (26) der Aussparung (27) und zum andem am einen Endabschnitt eines Federtellers (22) abstützt dessen anderer Endabschnitt an einer Schulter -insbesondere an einem Ringbund (21) des Verteilerkolbens (17) anliegt14. Pump according to claim 13, characterized in that the end face of the lifting disc ( 1 5) has a pot-like recess (27) and that the helical compression spring - (23) on the one hand on the inner wall (26) of the recess (27) and on one end section of a spring plate (22), the other end section of which rests on a shoulder, in particular on an annular collar (21) of the distributor piston (17)
EP86101107A 1985-02-28 1986-01-28 Fuel injection pump for internal-combustion engines Expired EP0192978B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3507014 1985-02-28
DE19853507014 DE3507014A1 (en) 1985-02-28 1985-02-28 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0192978A1 true EP0192978A1 (en) 1986-09-03
EP0192978B1 EP0192978B1 (en) 1988-05-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86101107A Expired EP0192978B1 (en) 1985-02-28 1986-01-28 Fuel injection pump for internal-combustion engines

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EP (1) EP0192978B1 (en)
JP (1) JPS61205371A (en)
DE (2) DE3507014A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0615063A1 (en) * 1993-03-06 1994-09-14 Robert Bosch Gmbh Fuel injection pump
WO1999051880A3 (en) * 1998-04-03 1999-12-29 Allen Norman Geldenhuys Multi-cylinder piston pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137073A1 (en) * 1991-11-12 1993-05-13 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4140256C2 (en) * 1991-12-06 1994-06-16 Bosch Gmbh Robert Venting device for a fuel tank of an internal combustion engine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1039309B (en) * 1956-12-19 1958-09-18 Bosch Gmbh Robert Fuel injection pump with distributor for multi-cylinder internal combustion engines
US3220217A (en) * 1961-12-20 1965-11-30 Mirkoz Muszaki Irodai Es Kozsz Driving mechanism for producing turning movements substantially without side forces

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1039309B (en) * 1956-12-19 1958-09-18 Bosch Gmbh Robert Fuel injection pump with distributor for multi-cylinder internal combustion engines
US3220217A (en) * 1961-12-20 1965-11-30 Mirkoz Muszaki Irodai Es Kozsz Driving mechanism for producing turning movements substantially without side forces

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0615063A1 (en) * 1993-03-06 1994-09-14 Robert Bosch Gmbh Fuel injection pump
US5474430A (en) * 1993-03-06 1995-12-12 Robert Bosch Gmbh Fuel injection pump
WO1999051880A3 (en) * 1998-04-03 1999-12-29 Allen Norman Geldenhuys Multi-cylinder piston pump

Also Published As

Publication number Publication date
DE3660192D1 (en) 1988-06-16
DE3507014A1 (en) 1986-08-28
JPS61205371A (en) 1986-09-11
EP0192978B1 (en) 1988-05-11

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