EP0261155B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0261155B1
EP0261155B1 EP87901397A EP87901397A EP0261155B1 EP 0261155 B1 EP0261155 B1 EP 0261155B1 EP 87901397 A EP87901397 A EP 87901397A EP 87901397 A EP87901397 A EP 87901397A EP 0261155 B1 EP0261155 B1 EP 0261155B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
projection
injection pump
control slide
guide groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP87901397A
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German (de)
French (fr)
Other versions
EP0261155A1 (en
Inventor
Josef Güntert
Walter Häfele
Johann Warga
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19863610928 external-priority patent/DE3610928A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0261155A1 publication Critical patent/EP0261155A1/en
Application granted granted Critical
Publication of EP0261155B1 publication Critical patent/EP0261155B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston

Definitions

  • the invention relates to a fuel injection pump according to the preamble of the main claim.
  • the quantity control or the start of injection control is carried out by controlling channels via which the pump work space can be connected to the suction space of the pump, namely by assigning control edges located on the pump piston to the control edges located in the control slide.
  • the rotary position of the control spool relative to the cylinder liner must be fixed, so that on the one hand the control spool maintains a certain fixed rotational position in relation to the rotatable pump piston and that on the other hand the control slide during basic adjustment, which is carried out by slightly turning the cylinder liner, which is then tightened is also rotated.
  • control slide In accordance with the task of such a control slide, it performs a large number of lifting cycles, so that a heavy wear load occurs on the guide surfaces of the anti-rotation device.
  • the control slide due to the fuel control provided by turning the pump piston, the control slide must be guided very precisely in the direction of rotation, so that a backlash between the control slide and the cylinder liner has a strong effect on the metering or spraying time accuracy of the fuel, with even a slight clearance being considerable Deviations of the actual control from the target control can result.
  • a pin is arranged on the wall of the recess of the cylinder liner, which engages in a longitudinal guide groove of the control slide, so that the axial displacement of the Control spool is secured against turning by pins and guide groove.
  • the pin In addition to the fact that the distance between the pin and the piston axis is relatively small, which also means that the lever distance preventing rotation is relatively short, the pin only has line contact with the groove wall or, with a slight inclination, point contact, which leads to relatively quick wear the consequence of the disadvantageous twist span or corresponding deterioration in the control accuracy of the fuel.
  • Another disadvantage is that such a pin can be attached relatively poorly in the wall of the recess, and loosening this pin directly on the pump and indirectly on the motor can lead to considerable damage.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the distance between the rotation guide point and the pump piston axis is increased, so that wear and thus play at the guide points have less effect with regard to the associated rotation error of the control slide.
  • the anti-rotation lock according to the invention can be produced very inexpensively and is extraordinarily stable and can be carried out with simple, customary working methods with regard to the fine machining of this fit between the nose and the guide groove. A detachment of the nose from the control slide is not possible, so that no consequential damage can occur.
  • the spool is not additionally weakened by a groove or is subject to dimensional changes as a result of a groove during heat treatment and during manufacture, so that the “dynamic” slide durability is very good.
  • the guide groove is designed as a slot-shaped opening in the wall of the recess in the cylinder liner.
  • a slot-like guide groove can be produced and machined in a simple manner, the machining in particular not having to take place within the recess of the cylinder liner.
  • Another advantage of this breakthrough in the wall of the cylinder liner is that it can be used for the fuel supply, so that additional connection bores can be saved in certain types of pumps in which these cylinder liners are arranged between an inlet line and the suction space.
  • the nose has a rectangular longitudinal cross-section, measured in an imaginary plane that runs parallel to a tangential plane of the control slide and perpendicular to the longitudinal symmetry plane of the nose, so that on the nose toward the lateral boundary surfaces of the guide groove, in Adjustment direction elongated guide surfaces are available.
  • these guide surfaces are flat and parallel to the boundary surfaces of the guide groove, so that a surface guide is created with a low Hertzian pressure and correspondingly low wear.
  • the guide surfaces are slightly spherical (slightly curved), so that there is surface contact between the lateral boundary surfaces of the guide groove and the guide surfaces of the nose under load.
  • this line contact or a surface contact, in which this surface has the greatest possible distance from the control slide can be achieved in that the nose tapers towards the control slide having.
  • Such tapering can be achieved, for example, by an undercut or undercut.
  • the nose is arranged on one side with respect to the direction of displacement of the control slide and the guide groove in the cylinder liner is correspondingly provided on one side.
  • FIG. 1 shows a longitudinal section through the parts of an injection pump relating to the invention, namely through a pump element including control slide of the first variant of the exemplary embodiment according to line II in FIG. 2
  • FIG. 2 shows a section along line 11-11 in FIG. 1
  • FIG. 4 shows a partial section along line IV-IV in FIG. 3.
  • FIGS. 1 and 2 only the pump element consisting of a pump piston 1 and a cylinder liner 2 and a control slide 3 are shown.
  • This assembly is known to be used in a fuel injection pump housing, in which the pump piston 1 is set in a reciprocating movement via a camshaft and against the force of a spring.
  • a flattening 4 is provided below, on which a control rod acts to twist this pump piston.
  • Another member, also not shown, which serves to control the fuel is an adjusting shaft which engages with a pin in a transverse groove 5 of the control slide 3 and axially displaces it on the pump piston 1.
  • the cylinder liner 2 consists of two parts which are inserted into one another at 6 and are connected to one another, for example, by brazing or heat shrinking.
  • a pump work chamber 7 in the cylinder liner 2 from which the fuel is conveyed to the internal combustion engine via valves and lines (not shown).
  • a central blind bore 8 is provided in the pump piston 1, which is crossed by a transverse bore 9 and a transverse bore 10.
  • the transverse bore 10 is connected to oblique grooves 11 provided on the lateral surface of the piston 1.
  • 3 radial bores 12 are provided in the ring slide.
  • the pump work chamber 7 is filled with fuel via the transverse bores 9, 10 and the axial bore 8 from a pump suction chamber 13, which in particular surrounds the control slide 3, during the suction stroke and in the bottom dead center position shown.
  • fuel then flows back into the suction space 13 via the longitudinal bore 8, the transverse bore 9, the transverse bore 10 and the control grooves 11 until the cross bore 9 is immersed in the cylinder liner 2 or until this control groove 11 is immersed in the control slide 3 or are. Only then does the actual injection to the internal combustion engine, which is dependent on the stroke position of the control slide 3, begins. This injection is interrupted when the oblique control edges 11 are controlled by the radial bores 12 of the control slide 3 during the delivery stroke.
  • the control slide 3 has on its rear side facing away from the transverse groove 5 a nose 14 which is guided in a slot-shaped opening 15 of the cylinder liner 2.
  • the nose 14 is arranged approximately in the middle with respect to the longitudinal extent of the control slide. The side surfaces of the nose and the guide surfaces of the opening 15 facing them run parallel.
  • the corresponding reference numerals are increased by the number 100, and in this respect reference is made to the parts already described in the first variant.
  • part of the pump housing 17 is shown, in addition to what is already shown in the first variant, in which an inlet pipe 18 for the fuel is installed, of which fuel via a radial bore 19 and a recess 21 in the pump housing 17 via the slot-shaped opening 115 can flow into the recess 113 of the cylinder liner 102, in which the control slide 103 is arranged to be axially movable.
  • the control slide 103 has a nose 114 which is guided in the slot-shaped opening 115.
  • a longitudinal bore 22 is also arranged with a larger cross section, which in the Recess 113 intersects, so that an open connection is created.
  • This longitudinal bore 22 forms the actual suction chamber of the pump together with the recesses 113 of the individual cylinder liners 102, which are usually arranged in series.
  • This suction chamber is supplied with fuel under low pressure by a feed pump, not shown.
  • the adjusting shaft 23 is arranged, on which pins 24 are provided which engage in the transverse groove 105 of the control slide 103.
  • An adjustment of this pin 24 is possible via an opening 25 in the pump housing 17, this opening 25 being closable by a plug, not shown.
  • Each of the individual control sliders 103 arranged in series is assigned a pin 24 and an opening 25, so that a whole series of such pins 24 are arranged on the adjusting shaft 23.
  • this second variant is offset asymmetrically downward with respect to the longitudinal extension of the control slide 103, with a corresponding arrangement of the opening 115. This prevents the control slide 103 from being installed the wrong way round, namely, for example, with the nose 114 upwards.
  • the nose 114 has an undercut at 26, so that the actual contact area between the nose 114 and the guide surfaces of the slot-shaped opening 115 only at the end of the undercut 26 Edge 27 begins.

Abstract

Fuel injection pump for internal combustion engines with at least one pump element (1, 2) and a control slide (3) which can move axially on the pump piston (1) and, in addition, a rotatable pump piston (1) for controlling the fuel, whereby the control slide (3) itself is prevented from rotation by a projection (14) which is inserted in a slotted groove (15) in the cylinder liner (2).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe nach der Gattung des Hauptanspruchs. Bei derartigen Hubschieberpumpen erfolgt die Mengensteuerung bzw. die Spritzbeginnsteuerung durch die Steuerung von Kanälen, über die der Pumpenarbeitsraum mit dem Saugraum der Pumpe verbindbar ist, nämlich durch die Zuordnung von am Pumpenkolben gelegenen Steuerkanten zu den im Steuerschieber gelegenen Steuerkanten. Aus diesem Grunde muss die Drehlage des Steuerschiebers zu der Zylinderbüchse fixiert werden, so dass einerseits der Steuerschieber gegenüber dem verdrehbaren Pumpenkolben eine bestimmte fixierte Drehlage einhält und dass andererseits bei der Grundjustierung, die durch leichtes Verdrehen der Zylinderbüchse erfolgt, welche danach festgespannt wird, der Steuerschieber mitgedreht wird.The invention relates to a fuel injection pump according to the preamble of the main claim. In such slide valve pumps, the quantity control or the start of injection control is carried out by controlling channels via which the pump work space can be connected to the suction space of the pump, namely by assigning control edges located on the pump piston to the control edges located in the control slide. For this reason, the rotary position of the control spool relative to the cylinder liner must be fixed, so that on the one hand the control spool maintains a certain fixed rotational position in relation to the rotatable pump piston and that on the other hand the control slide during basic adjustment, which is carried out by slightly turning the cylinder liner, which is then tightened is also rotated.

Entsprechend der Aufgabe eines derartigen Steuerschiebers führt dieser sehr viele Hubspiele aus, so dass an den Führungsflächen der Verdrehsicherung eine starke Abnutzungsbelastung auftritt. Hinzu kommt, dass aufgrund der durch Verdrehen des Pumpenkolbens gegebenen Kraftstoffsteuerung der Steuerschieber in Verdrehrichtung sehr exakt geführt sein muss, so dass ein Verdrehspiel zwischen Steuerschieber und Zylinderbüchse sich stark auf die Zumess- bzw. Spritzzeitgenauigkeit des Kraftstoffes auswirkt, wobei schon ein geringes Spiel zu erheblichen Abweichungen der Iststeuerung von der Sollsteuerung führen kann.In accordance with the task of such a control slide, it performs a large number of lifting cycles, so that a heavy wear load occurs on the guide surfaces of the anti-rotation device. In addition, due to the fuel control provided by turning the pump piston, the control slide must be guided very precisely in the direction of rotation, so that a backlash between the control slide and the cylinder liner has a strong effect on the metering or spraying time accuracy of the fuel, with even a slight clearance being considerable Deviations of the actual control from the target control can result.

Bei einer bekannten Kraftstoffeinspritzpumpe der gattungsgemässen Art (EP-A-0 181 402, Art. 54(3)) ist an der Wand der Ausnehmung der Zylinderbüchse ein Zapfen angeordnet, der in eine Führungslängsnut des Steuerschiebers greift, so dass bei der axialen Verschiebung des Steuerschiebers dieser durch Zapfen und Führungsnut gegen Verdrehen gesichert ist. Abgesehen davon, dass der Abstand zwischen Zapfen und Kolbenachse verhältnismässig klein ist, wodurch auch der die Verdrehung verhindernde Hebelabstand verhältnismässig kurz ist, weist der Zapfen zur Nutenwandung hin nur Linien- oder bei geringer Schräglage Punktberührung auf, was zu einer verhältnismässig schnellen Abnutzung führt, mit der Folge des nachteiligen Verdrehspiefs bzw. entsprechender Verschlechterung der Steuergenauigkeit des Kraftstoffes. Ein weiterer Nachteil besteht darin, dass ein derartiger Zapfen verhältnismässig schlecht in der Wandung der Ausnehmung befestigt werden kann, wobei ein Lösen dieses Zapfens unmittelbar an der Pumpe und mittelbar am Motor zu erheblichen Schäden führen kann.In a known fuel injection pump of the generic type (EP-A-0 181 402, Art. 54 (3)) a pin is arranged on the wall of the recess of the cylinder liner, which engages in a longitudinal guide groove of the control slide, so that the axial displacement of the Control spool is secured against turning by pins and guide groove. In addition to the fact that the distance between the pin and the piston axis is relatively small, which also means that the lever distance preventing rotation is relatively short, the pin only has line contact with the groove wall or, with a slight inclination, point contact, which leads to relatively quick wear the consequence of the disadvantageous twist span or corresponding deterioration in the control accuracy of the fuel. Another disadvantage is that such a pin can be attached relatively poorly in the wall of the recess, and loosening this pin directly on the pump and indirectly on the motor can lead to considerable damage.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemässe Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Hauptanspruches hat demgegenüber den Vorteil, dass der Abstand der Verdrehführungsstelle zur Pumpenkolbenachse vergrössert ist, so dass sich Abnutzungen und damit Spiel an den Führungsstellen bezüglich des damit verbundenen Verdrehfehlers des Steuerschiebers weniger auswirken. Je grösser der Abstand der Verdrehführung zur Kolbenachse ist, desto kleiner ist bei einem bestimmten Verdrehspiel der Steuerfehler. Bei doppelt langer «Hebelführung» ist der Steuerfehler bei gleichem Verdrehspiel nur halb so gross. Ein weiterer Vorteil besteht darin, dass die erfindungsgemässe Verdrehsicherung sehr kostengünstig herstellbar und ausserordentlich stabil ist und in bezug auf die Feinbearbeitung dieser Passung zwischen Nase und Führungsnut mit einfachen üblichen Arbeitsmethoden erfolgen kann. Ein Loslösen der Nase von dem Steuerschieberist nicht möglich, so dass auch keine diesbezüglichen Folgeschäden entstehen können. Ein weiterer Vorteil besteht darin, dass der Steuerschieber nicht zusätzlich durch eine Nut geschwächt wird oder infolge einer Nut bei der Warmbehandlung und während der Herstellung Massänderungen unterworfen ist, so dass die «dynamische» Schieberhaltbarkeit sehr gut ist.The fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the distance between the rotation guide point and the pump piston axis is increased, so that wear and thus play at the guide points have less effect with regard to the associated rotation error of the control slide. The greater the distance between the twist guide and the piston axis, the smaller the control error for a certain twist play. If the lever control is twice as long, the control error is only half as great with the same backlash. Another advantage is that the anti-rotation lock according to the invention can be produced very inexpensively and is extraordinarily stable and can be carried out with simple, customary working methods with regard to the fine machining of this fit between the nose and the guide groove. A detachment of the nose from the control slide is not possible, so that no consequential damage can occur. Another advantage is that the spool is not additionally weakened by a groove or is subject to dimensional changes as a result of a groove during heat treatment and during manufacture, so that the “dynamic” slide durability is very good.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist die Führungsnut als schlitzförmiger Durchbruch in der Wandung der Ausnehmung der Zylinderbüchse ausgebildet. Eine solche schlitzartige Führungsnut ist in einfacher Weise herstellbar und bearbeitbar, wobei besonders das Bearbeiten nicht innerhalb der Ausnehmung der Zylinderbüchse erfolgen muss. Ein weiterer Vorteil dieses Durchbruchs in der Wandung der Zylinderbüchse besteht darin, dass er für die Kraftstoffzuführung verwendbar ist, so dass bei bestimmten Pumpentypen, bei denen diese Zylinderbüchsen zwischen einer Zulaufleitung und dem Saugraum angeordnet sind, zusätzliche Verbindungsbohrungen eingespart werden können.According to an advantageous embodiment of the invention, the guide groove is designed as a slot-shaped opening in the wall of the recess in the cylinder liner. Such a slot-like guide groove can be produced and machined in a simple manner, the machining in particular not having to take place within the recess of the cylinder liner. Another advantage of this breakthrough in the wall of the cylinder liner is that it can be used for the fuel supply, so that additional connection bores can be saved in certain types of pumps in which these cylinder liners are arranged between an inlet line and the suction space.

Nach einer weiteren Ausgestaltung der Erfindung weist die Nase einen rechteckigen Längsquerschnitt auf, gemessen in einer gedachten Ebene, die parallel zu einer Tangentialebene des Steuerschiebers und senkrecht zu der Längssymmetrieebene der Nase verläuft, so dass an der Nase zu den seitlichen Begrenzungsflächen der Führungsnut hin, in Verstellrichtung längliche Führungsflächen vorhanden sind. Nach einer Ausgestaltung der Erfindung sind diese Führungsflächen eben und parallel zu den Begrenzungsflächen der Führungsnut ausgebildet, so dass eine Flächenführung entsteht, mit geringer Hertzscher Pressung und entsprechend geringem Verschleiss. Nach einer anderen Ausgestaltung der Erfindung sind die Führungsflächen leicht ballig (geringfügig gewölbt) ausgebildet, so dass unter Belastung eine Flächenberührung zwischen den seitlichen Begrenzungsflächen der Führungsnut und den Führungsflächen der Nase besteht. Derartige Anordnungen erlauben eine hohe Kraftübertragung bei verhältnismässig geringer Hertzscher Pressung und damit geringer Abnutzung. Erfindungsgemäss kann diese Linienberührung oder auch eine Flächenberührung, bei der diese Fläche einen möglichst grossen Abstand zum Steuerschieber hat, dadurch erreicht werden, dass die Nase zum Steuerschieber hin eine Verjüngung aufweist. Eine solche Verjüngung kann beispielsweise durch einen Freistich oder Hinterstich erreicht werden.According to a further embodiment of the invention, the nose has a rectangular longitudinal cross-section, measured in an imaginary plane that runs parallel to a tangential plane of the control slide and perpendicular to the longitudinal symmetry plane of the nose, so that on the nose toward the lateral boundary surfaces of the guide groove, in Adjustment direction elongated guide surfaces are available. According to one embodiment of the invention, these guide surfaces are flat and parallel to the boundary surfaces of the guide groove, so that a surface guide is created with a low Hertzian pressure and correspondingly low wear. According to another embodiment of the invention, the guide surfaces are slightly spherical (slightly curved), so that there is surface contact between the lateral boundary surfaces of the guide groove and the guide surfaces of the nose under load. Such arrangements allow high power transmission with a relatively low Hertzian pressure and thus less wear. According to the invention, this line contact or a surface contact, in which this surface has the greatest possible distance from the control slide, can be achieved in that the nose tapers towards the control slide having. Such tapering can be achieved, for example, by an undercut or undercut.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist die Nase in bezug auf die Verschieberichtung des Steuerschiebers einseitig an diesem angeordnet und es ist entsprechend die Führungsnut in der Zylinderbüchse einseitig vorhanden. Hierdurch wird erreicht, dass bei der Montage der Kraftstoffeinspritzpumpe der Steuerschieber stets in die richtige Einbaulage eingesetzt wird. Bei falschem Einbau des Steuerschiebers, wie es beispielsweise bei in Längsrichtung symmetrischer Anordnung der Nase am Steuerschieber vorkommen kann, wird dieses meist erst festgestellt, wenn die Kraftstoffeinspritzpumpe eingestellt werden soll und die Kraftstoffsteuerung überhaupt nicht oder völlig falsch arbeitet. Dies führt zu hohen Nacharbeitungskosten in der Fertigung wie auch bei Falscheinbau im Service, was durch die erfindungsgemässe Ausgestaltung unterbunden wird.According to a further advantageous embodiment of the invention, the nose is arranged on one side with respect to the direction of displacement of the control slide and the guide groove in the cylinder liner is correspondingly provided on one side. This ensures that when the fuel injection pump is installed, the control spool is always inserted in the correct installation position. If the control spool is installed incorrectly, as can occur, for example, if the nose on the control spool is arranged symmetrically in the longitudinal direction, this is usually only determined when the fuel injection pump is to be adjusted and the fuel control system is not working at all or is working completely incorrectly. This leads to high reworking costs in production as well as in incorrect installation in service, which is prevented by the configuration according to the invention.

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

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist mit zwei Varianten in der Zeichnung dargestellt und wird im folgenden näher beschrieben. Es zeigen Fig. 1 einen Längsschnitt, durch die die Erfindung betreffenden Teile einer Einspritzpumpe, nämlich durch ein Pumpenelement einschliesslich Steuerschieber der ersten Variante des Ausführungsbeispiels nach Linie I-I in Fig. 2, Fig. 2 einen Schnitt nach Linie 11-11 in Fig. 1, Fig. 3 einen Fig. 1 entsprechenden Schnitt durch die zweite Variante des Ausführungsbeispiels und Fig. 4 einen Teilschnitt nach Linie IV-IV in Fig. 3.An embodiment of the object of the invention is shown with two variants in the drawing and will be described in more detail below. 1 shows a longitudinal section through the parts of an injection pump relating to the invention, namely through a pump element including control slide of the first variant of the exemplary embodiment according to line II in FIG. 2, FIG. 2 shows a section along line 11-11 in FIG. 1 3 shows a section corresponding to FIG. 1 through the second variant of the exemplary embodiment and FIG. 4 shows a partial section along line IV-IV in FIG. 3.

Beschreibung des Ausführungsbeispiels in zwei VariantenDescription of the embodiment in two variants

Bei der in Fig. 1 und 2 dargestellten Variante des Ausführungsbeispiels ist jeweils nur das aus einem Pumpenkolben 1 und einer Zylinderbüchse 2 bestehende Pumpenelement sowie ein Steuerschieber 3 dargestellt. Diese Baueinheit wird bekannterweise in ein Kraftstoffeinspritzpumpengehäuse eingesetzt, worin über eine Nockenwelle und entgegen der Kraft einer Feder der Pumpenkolben 1 in eine hin- und hergehende Bewegung versetzt wird. An dem Pumpenkolben 1 ist weiter unten eine Abflachung 4 vorgesehen, an der eine Regelstange zu Verdrehung dieses Pumpenkolbens angreift. Ein weiteres ebenfalls nicht dargestelltes, der Kraftstoffsteuerung dienendes Glied ist eine Verstellwelle, die mit einem Zapfen in eine Quernut 5 des Steuerschiebers 3 greift und diesen axial auf dem Pumpenkolben 1 verschiebt. Die Zylinderbüchse 2 besteht bei dieser Variante des ausgewählten Ausführungsbeispiels aus zwei Teilen, die bei 6 ineinandergesteckt sind und beispielsweise durch Hartlöten oder Warmschrumpfen miteinanderverbunden sind. Oberhalb des Pumpenkolbens 1 ist in der Zylinderbüchse 2 ein Pumpenarbeitsraum 7 vorhanden, aus dem der Kraftstoff über nicht dargestellte Ventile und Leitungen zur Brennkraftmaschine gefördert wird. Weiterhin ist im Pumpenkolben 1 eine zentrale Sackbohrung 8 vorgesehen, die durch eine Querbohrung 9 und eine Querbohrung 10 gekreuzt wird. Die Querbohrung 10 ist mit auf der Mantelfläche des Kolbens 1 vorhandenen Schrägnuten 11 verbunden. Ausserdem sind im Ringschieber 3 Radialbohrungen 12 vorgesehen.In the variant of the exemplary embodiment shown in FIGS. 1 and 2, only the pump element consisting of a pump piston 1 and a cylinder liner 2 and a control slide 3 are shown. This assembly is known to be used in a fuel injection pump housing, in which the pump piston 1 is set in a reciprocating movement via a camshaft and against the force of a spring. On the pump piston 1, a flattening 4 is provided below, on which a control rod acts to twist this pump piston. Another member, also not shown, which serves to control the fuel is an adjusting shaft which engages with a pin in a transverse groove 5 of the control slide 3 and axially displaces it on the pump piston 1. In this variant of the selected exemplary embodiment, the cylinder liner 2 consists of two parts which are inserted into one another at 6 and are connected to one another, for example, by brazing or heat shrinking. Above the pump piston 1, there is a pump work chamber 7 in the cylinder liner 2, from which the fuel is conveyed to the internal combustion engine via valves and lines (not shown). Furthermore, a central blind bore 8 is provided in the pump piston 1, which is crossed by a transverse bore 9 and a transverse bore 10. The transverse bore 10 is connected to oblique grooves 11 provided on the lateral surface of the piston 1. In addition, 3 radial bores 12 are provided in the ring slide.

Der Pumpenarbeitsraum 7 wird über die Querbohrungen 9, 10 und die Axialbohrung 8 aus einem Pumpensaugraum 13, der insbesondere den Steuerschieber 3 umgibt, während des Saughubs und in der dargestellten unteren Totpunktlage mit Kraftstoff gefüllt. Bei dem Druckhub strömt dann über die Längsbohrung 8, die Querbohrung 9, die Querbohrung 10 und die Steuernuten 11 so lange Kraftstoff zurück in den Saugraum 13, bis die Querbohrung 9 in die Zylinderbüchse 2 bzw. bis diese Steuernuten 11 in den Steuerschieber 3 getaucht ist bzw. sind. Danach beginnt erst die eigentliche, somit von der Hublage des Steuerschiebers 3 abhängige, Einspritzung zur Brennkraftmaschine. Diese Einspritzung wird unterbrochen, wenn die schrägen Steuerkanten 11 während des Förderhubs durch die Radialbohrungen 12 des Steuerschiebers 3 auf gesteuert werden. Danach strömt der Kraftstoff aus dem Pumpenarbeitsraum 7 über die Axialbohrung 8, die Querbohrung 10, die Schrägnuten 11 und die Radialbohrungen 12 zurück in den Saugraum 13. Je nach Drehlage des Pumpenkolbens 1, d. h. je nach relativer Lage der Schrägnuten 11 zu den Radialbohrungen 12, ist dieser effektive zur Einspritzung teilweise Förderhubabschnitt unterschiedlich.The pump work chamber 7 is filled with fuel via the transverse bores 9, 10 and the axial bore 8 from a pump suction chamber 13, which in particular surrounds the control slide 3, during the suction stroke and in the bottom dead center position shown. During the pressure stroke, fuel then flows back into the suction space 13 via the longitudinal bore 8, the transverse bore 9, the transverse bore 10 and the control grooves 11 until the cross bore 9 is immersed in the cylinder liner 2 or until this control groove 11 is immersed in the control slide 3 or are. Only then does the actual injection to the internal combustion engine, which is dependent on the stroke position of the control slide 3, begins. This injection is interrupted when the oblique control edges 11 are controlled by the radial bores 12 of the control slide 3 during the delivery stroke. Then the fuel flows out of the pump working space 7 via the axial bore 8, the transverse bore 10, the oblique grooves 11 and the radial bores 12 back into the suction space 13. Depending on the rotational position of the pump piston 1, i. H. depending on the relative position of the oblique grooves 11 to the radial bores 12, this effective delivery stroke section for injection is different.

Der Steuerschieber 3 weist auf seiner der Quernut 5 abgewandten Rückseite eine Nase 14 auf, die in einem schlitzförmigen Durchbruch 15 der Zylinderbüchse 2 geführt ist. Die Nase 14 ist in bezug auf die Längsausdehnung des Steuerschiebers 3 etwa in der Mitte angeordnet. Die Seitenflächen der Nase und die diesen zugewandten Führungsflächen des Durchbruchs 15 verlaufen parallel.The control slide 3 has on its rear side facing away from the transverse groove 5 a nose 14 which is guided in a slot-shaped opening 15 of the cylinder liner 2. The nose 14 is arranged approximately in the middle with respect to the longitudinal extent of the control slide. The side surfaces of the nose and the guide surfaces of the opening 15 facing them run parallel.

Bei der in den Fig. 3 und 4 dargestellten zweiten Variante des Ausführungsbeispiels sind die entsprechenden Bezugsziffern um die Zahl 100 erhöht und es wird insofern auf die bereits in der ersten Variante beschriebenen Teile Bezug genommen. Über das bereits in der ersten Variante Gezeigte, ist bei dieser Variante ein Teil des Pumpengehäuses 17 gezeigt, in dem ein Zulaufrohr 18 für den Kraftstoff eingebaut ist, von dem über eine Radialbohrung 19 und eine Ausnehmung 21 im Pumpengehäuse 17 Kraftstoff über den schlitzförmigen Durchbruch 115 in die Ausnehmung 113 der Zylinderbüchse 102 strömen kann, in der der Steuerschieber 103 axial beweglich angeordnet ist. Auch bei dieser Variante weist der Steuerschieber 103 eine Nase 114 auf, die in dem schlitzförmigen Durchbruch 115 geführt ist. Im Pumpengehäuse 17 ist ausserdem eine Längsbohrung 22 grösseren Querschnitts angeordnet, die in die Ausnehmung 113 schneidet, so dass dadurch eine offene Verbindung entsteht. Diese Längsbohrung 22 bildet den eigentlichen Saugraum der Pumpe gemeinsam mit den Ausnehmungen 113 der einzelnen, meist in Reihe angeordneten, Zylinderbüchsen 102. Dieser Saugraum wird durch eine nicht dargestellte Förderpumpe mit Kraftstoff unter niederem Druck versorgt.In the second variant of the exemplary embodiment illustrated in FIGS. 3 and 4, the corresponding reference numerals are increased by the number 100, and in this respect reference is made to the parts already described in the first variant. In this variant, part of the pump housing 17 is shown, in addition to what is already shown in the first variant, in which an inlet pipe 18 for the fuel is installed, of which fuel via a radial bore 19 and a recess 21 in the pump housing 17 via the slot-shaped opening 115 can flow into the recess 113 of the cylinder liner 102, in which the control slide 103 is arranged to be axially movable. In this variant too, the control slide 103 has a nose 114 which is guided in the slot-shaped opening 115. In the pump housing 17, a longitudinal bore 22 is also arranged with a larger cross section, which in the Recess 113 intersects, so that an open connection is created. This longitudinal bore 22 forms the actual suction chamber of the pump together with the recesses 113 of the individual cylinder liners 102, which are usually arranged in series. This suction chamber is supplied with fuel under low pressure by a feed pump, not shown.

In der Längsbohrung 22 ist die Verstellwelle 23 angeordnet, an der Zapfen 24 vorhanden sind, die in die Quernut 105 des Steuerschiebers 103 greifen. Eine Justierung dieses Zapfens 24 ist über eine Öffnung 25 im Pumpengehäuse 17 möglich, wobei diese Öffnung 25 durch einen nicht dargestellten Stopfen verschliessbar ist. So ist jedem der einzelnen, in Reihe angeordneten Steuerschiebern 103 ein Zapfen 24 und eine Öffnung 25 zugeordnet, so dass an der Verstellwel le 23 eine ganze Reihe von derartigen Zapfen 24 angeordnet sind.In the longitudinal bore 22, the adjusting shaft 23 is arranged, on which pins 24 are provided which engage in the transverse groove 105 of the control slide 103. An adjustment of this pin 24 is possible via an opening 25 in the pump housing 17, this opening 25 being closable by a plug, not shown. Each of the individual control sliders 103 arranged in series is assigned a pin 24 and an opening 25, so that a whole series of such pins 24 are arranged on the adjusting shaft 23.

Der wesentliche Unterschied dieser zweiten Variante zur ersten Variante besteht darin, dass die Nase 114 in bezug auf die Längsausdehnung des Steuerschiebers 103 asymmetrisch nach unten versetzt ist, bei entsprechender Lageanordnung des Durchbruchs 115. Hierdurch wird unterbunden, dass der Steuerschieber 103 falsch herum eingebaut wird, nämlich beispielsweise mit der Nase 114 nach oben.The main difference between this second variant and the first variant is that the lug 114 is offset asymmetrically downward with respect to the longitudinal extension of the control slide 103, with a corresponding arrangement of the opening 115. This prevents the control slide 103 from being installed the wrong way round, namely, for example, with the nose 114 upwards.

Ein weiterer Unterschied zu der ersten Variante besteht wie aus Fig. 4 entnehmbar darin, dass die Nase 114 bei 26 eine Hinterschneidung aufweist, so dass die tatsächliche Berührungsfläche zwischen Nase 114 und den Führungsflächen des schlitzförmigen Durchbruchs 115 erst an der das Ende der Hinterschneidung 26 bildenden Kante 27 beginnt.Another difference from the first variant, as can be seen from FIG. 4, is that the nose 114 has an undercut at 26, so that the actual contact area between the nose 114 and the guide surfaces of the slot-shaped opening 115 only at the end of the undercut 26 Edge 27 begins.

Claims (10)

1. Fuel injection pump for internal combustion engines, having at least one pump element whose pump cylinder, designed as a cylinder liner (2, 102), is secured in a corresponding bore of the pump housing and whose pump piston (1) is driven for a reciprocating working stroke and can be rotated for controlling the fuel, and having at least one control slide (3,103) which is present on the pump piston (1) inside a recess (13, 113) of the cylinder liner (2, 102), has an anti-rotation means and is axially displaceable on the pump piston (1) for controlling the fuel, characterized in that a projection (14, 114), protruding radially from the control slide (3,103), and a guide groove (15, 115) in the cylinder liner (2,102) serve as an anti-rotation means, into which guide groove (15, 115) the projection (14, 114) engages, and that the guide groove (15,115) is arranged in the wall of the recess (13, 113) of the cylinder liner (2, 102).
2. Fuel injection pump according to Claim 1, characterized in that the guide groove is designed as a slotted aperture (15, 115) in the wall of the recess (13, 113) of the cylinder liner (2, 102).
3. Fuel injection pump according to Claim 1 or 2, characterized in that the projection (14, 114) has a rectangular cross-section, measured in an imaginary plane which runs parallel to a tangential plane of the control slide and perpendicularly to the longitudinal plane of symmetry of the projection (14, 114) so that there are guide surfaces on the projection towards the lateral boundary surfaces of the guide groove (15, 115).
4. Fuel injection pump according to Claim 3, characterized in that the guide surfaces are formed flat so that there is surface contact between the lateral boundary surfaces of the guide groove (15, 115) and the guide surfaces of the projection (14, 114).
5. Fuel injection pump according to Claim 3, characterized in that the guide surfaces are found slightly crowned so that there is line contact between the lateral boundary surfaces of the guide groove (15, 115) and the guide surfaces of the projection (14, 114).
6. Fuel injection pump according to any of the preceding claims, characterized in that the projection (114) has a taper (26) towards the control slide (103).
7. Fuel injection pump according to any of the preceding claims, characterized in that the projection (114) with regard to the displacement direction of the control slide (103), is arranged on one side (asymmetrically) on the latter.
8. Fuel injection pump according to Claim 7, characterized in that the guide groove (115) is likewise formed on one side in accordance with the position of the projection.
9. Fuel injection pump according to any of Claims 2 to 8, characterized in that the aperture (115) additionally serves the fuel supply.
10. Fuel injection pump according to any of the preceding claims, characterized in that there is a transverse groove (105) on the control slide (103) for the engagement of a driving pin (24) used for the axial displacement, and that this transverse groove, with regard to the displacement direction of the control slide (103), is arranged on one side (asymmetrically) on the latter.
EP87901397A 1986-03-24 1987-03-19 Fuel injection pump for internal combustion engines Expired EP0261155B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3610928 1986-03-24
DE19863610928 DE3610928A1 (en) 1986-03-24 1986-03-24 Fuel injection pump for internal combustion engines
DE19863630647 DE3630647A1 (en) 1986-03-24 1986-09-09 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3630647 1986-09-09

Publications (2)

Publication Number Publication Date
EP0261155A1 EP0261155A1 (en) 1988-03-30
EP0261155B1 true EP0261155B1 (en) 1989-06-14

Family

ID=25842517

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901397A Expired EP0261155B1 (en) 1986-03-24 1987-03-19 Fuel injection pump for internal combustion engines

Country Status (6)

Country Link
US (1) US4850822A (en)
EP (1) EP0261155B1 (en)
JP (1) JPH086660B2 (en)
KR (1) KR940008283B1 (en)
DE (2) DE3630647A1 (en)
WO (1) WO1987005970A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3902670A1 (en) * 1989-01-30 1990-08-02 Voest Alpine Automotive INJECTION PUMP FOR DIESEL ENGINES
DE4041656A1 (en) * 1990-12-22 1992-07-02 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4041503C2 (en) * 1990-12-22 2001-02-15 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
DE4132502C2 (en) * 1991-09-30 2001-09-27 Bosch Gmbh Robert Fuel injection pump
JP2003262172A (en) * 2002-03-06 2003-09-19 Bosch Automotive Systems Corp Injection pump, and fuel supply device for diesel engine provided with the same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1132382B (en) * 1960-12-02 1962-06-28 Friedmann & Maier Ag Injection pump for internal combustion engines
FR1446048A (en) * 1964-05-25 1966-07-15 Bryce Berger Ltd Advanced pump for liquid fuel injection
AU563901B2 (en) * 1984-05-08 1987-07-23 Bosch Automotive Systems Corporation Fuel injection pump and method of adjusting the same pump
JPS61123756A (en) * 1984-11-16 1986-06-11 Diesel Kiki Co Ltd Fuel injection pump

Also Published As

Publication number Publication date
KR880701328A (en) 1988-07-26
US4850822A (en) 1989-07-25
DE3630647A1 (en) 1988-02-11
DE3760251D1 (en) 1989-07-20
KR940008283B1 (en) 1994-09-09
EP0261155A1 (en) 1988-03-30
JPS63503077A (en) 1988-11-10
JPH086660B2 (en) 1996-01-29
WO1987005970A1 (en) 1987-10-08

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