EP0153491A1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

Info

Publication number
EP0153491A1
EP0153491A1 EP84116244A EP84116244A EP0153491A1 EP 0153491 A1 EP0153491 A1 EP 0153491A1 EP 84116244 A EP84116244 A EP 84116244A EP 84116244 A EP84116244 A EP 84116244A EP 0153491 A1 EP0153491 A1 EP 0153491A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve seat
plate
seat body
injection pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP84116244A
Other languages
German (de)
French (fr)
Inventor
Walter Ing. Häfele
Reinhard Dipl.-Ing. Schwartz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0153491A1 publication Critical patent/EP0153491A1/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines of the type specified in the preamble of claim 1.
  • the two valves are combined to form a double-acting valve with a single plate-shaped, resilient circular valve plate having a central passage, which lies in the area of its outer circumference on a first valve seat and in the area of its passage on a second valve seat which is arranged opposite the first valve seat.
  • the valve plate lifts off the valve seat on the outer circumference in the conveying direction and opens in the opposite direction in the area of its passage.
  • the central passage of the valve plate lies with play around a pin, so that between The pin and inner wall of the valve plate set a narrow annular gap with throttling effect (DE-OS 18 15 254).
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage, on the one hand, of being extremely flat like the known double-acting valve and, on the other hand, of offering the advantages of a two-valve arrangement, namely the sufficiently precise setting of the opening pressure and the clean closing and opening of the valves both in the funding and in the relief phase. Due to the design, extremely small dead spaces and the associated extremely low harmful volume, a high injection pressure can be achieved.
  • the fuel injection pump for an internal combustion engine which can be seen in detail in longitudinal section in FIG. 1, has a pump housing 10 with a bore 11 in which, on the one hand, a cylinder liner 12, in which a pump piston 13 is guided axially displaceably, and on the other hand, a two-valve arrangement, hereinafter referred to as a constant pressure valve 14 , is used.
  • Pump piston 13, cylinder liner 12 and the lower end face 15 of the constant pressure valve 14 delimit a pump working space 16 of the fuel injection pump.
  • a connection channel 17 opens for a pressure line leading to an injection nozzle, not shown.
  • the constant pressure valve 14 has, in spatial succession, a pressure valve 18 which opens in the fuel delivery direction, that is to say from the pump working chamber 16 to the connecting duct 17, and a relief valve 19 which opens in the opposite direction.
  • the pressure valve 18 controls the K raftstoff begang to the injection nozzle, while the relief valve is necessary to prevent so-called afterdrip the injection nozzle and the avoidance of cavitation damage due to pressure waves 19, which develop during the closing of the injector and be reflected several times at closed discharge line.
  • the pressure valve 18 is designed as a plate or plate seat valve. It has a valve seat body 20, a valve plate 21 designed as an annular disk and a flat-conical disk-like valve closing spring 22 with a central passage 24.
  • the valve closing spring 22 is designed here as a plate spring (FIG. 2).
  • the valve seat body 20 has a plurality of through bores 25 which are arranged at a radial distance from the valve axis and offset in the circumferential direction, which are open to the pump working chamber 16 on the one hand and can be covered by the valve plate 21 on the other hand.
  • the valve closing spring 22 lies in the region of its passage 24 on the valve plate 21 and presses against a valve seat 26 on the end face 27 of a connecting piece 28 in the vicinity of its outer periphery, as a result of which the valve plate 21 is pressed onto the valve seat body 20.
  • the connection piece 28 carries the central connection channel 17, the opening of which in the front face 27 is essentially aligned with the passage 24 of the valve closing spring 22 and the ring opening 29 of the valve plate 21 designed as an annular disk. Due to this design, the valve closing spring 22 of the pressure valve 18 also forms the valve closing or opening member of the relief valve 19.
  • a spacer ring 30 is arranged, in the ring opening 31, the valve plate 21 is centered.
  • an axial groove 33 is arranged, which is in liquid-conducting connection with a radial groove 34, which at the same time the End face 35 of the valve seat body 20 forming the valve seat is arranged and opens into one of the through bores 2.
  • This radial groove 34 acts in the relief phase, that is to say when the relief valve 19 is open, as a backflow throttle for the fuel from the connection channel 17 to the pump work space 16.
  • the spacer ring 30 can be designed in one piece with both the connection piece 28 and the valve seat body 20, but is made from manufacturing reasons preferably carried out as a single part.
  • the connector 28, the spacer ring 30 and the valve seat body 20 are surrounded on the outside by a high-pressure seal 36, which on the free end face 15 of the valve seat body. 20 overlaps with a flange 37 and is positively connected to the connector 28 by beads 38.
  • connection channel 17 If, however, the pressure in the connection channel 17 is higher than the spring force of the plate spring 23, which is now effective as a valve member for the relief valve 19, this springs on the outer circumference of its valve seat 26 on the connection piece 28, so that fuel now flows in the opposite direction from the connection channel 17 Via the axial groove 33, the radial groove 34 acting as a backflow throttle and a through hole 25 can flow to the pump working space 16.
  • the relief valve 19 thus determines the standing pressure remaining in the pressure line to the injection nozzle, and the backflow throttle 34 dampens the relief process in the desired manner.

Abstract

To achieve an extremely flat construction, on the one hand, and sufficiently precise setting of the response instant, on the other hand, in a fuel injection pump for internal-combustion engines having a two-valve arrangement comprising a delivery valve (18) and a relief valve (19), the two valves (18, 19) are arranged spatially in series with mutually facing valve seats (35, 26) and the delivery valve (18) is designed as a plate valve. The valve closing spring (22) of the plate valve (18) is a flat-cone disc-shaped cup spring and simultaneously forms the valve member of the relief valve (19) (Fig. 1). <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen der im Oberbegriff des Anspruchs 1 angegebenen Gattung.The invention relates to a fuel injection pump for internal combustion engines of the type specified in the preamble of claim 1.

Bei einer bekannten Kraftstoffeinspritzpumpe dieser Art sind die beiden Ventile zu einem doppeltwirkenden Ventil mit einer einzigen plattenförmigen, federnden und einen zentralen Durchlaß aufweisenden kreisförmigen Ventilplatte zusammengefaßt, die im Bereich ihres Außenumfangs an einem ersten Ventilsitz und im Bereich ihres Durchlasses an einem zweiten Ventilsitz anliegt, der dem ersten Ventilsitz gegenüberliegend angeordnet ist. Die Ventilplatte hebt in Förderrichtung am Außenumfang vom Ventilsitz ab und öffnet in Gegenrichtung im Bereich ihres Durchlasses. Zur Erzielung einer Drosselwirkung in Rückströmrichtung, also entgegen der Förderrichtung,liegt der zentrale Durchlaß der Ventilplatte mit Spiel um einen Zapfen, so daß sich zwischen Zapfen und Innenwand der Ventilplatte ein schmaler Ringspalt mit Drosselwirkung einstellt (DE-OS 18 15 254).In a known fuel injection pump of this type, the two valves are combined to form a double-acting valve with a single plate-shaped, resilient circular valve plate having a central passage, which lies in the area of its outer circumference on a first valve seat and in the area of its passage on a second valve seat which is arranged opposite the first valve seat. The valve plate lifts off the valve seat on the outer circumference in the conveying direction and opens in the opposite direction in the area of its passage. To achieve a throttling effect in the backflow direction, that is, counter to the conveying direction, the central passage of the valve plate lies with play around a pin, so that between The pin and inner wall of the valve plate set a narrow annular gap with throttling effect (DE-OS 18 15 254).

Bei einem solchen doppeltwirkenden Ventil läßt sich zum einen der Öffnungsdruck nicht ausreichend genau einstellen und zum anderen wird eine gewisse Neigung zum Flattern während der Entlastungsphase beobachtet.With such a double-acting valve, on the one hand the opening pressure cannot be set with sufficient accuracy and on the other hand a certain tendency to flutter is observed during the relief phase.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, einerseits gleich extrem flach zu bauen wie das bekannte doppeltwirkende Ventil und andererseits die Vorzüge einer Zweiventilanordnung zu bieten, nämlich das hinreichend genaue Einstellen des Öffnungsdruckes und das saubere Schließen und Öffnen der Ventile sowohl in der Förder- als auch in der Entlastungsphase. Durch konstruktiv bedingt extrem kleine Toträume und damit verbundenen äußerst geringem schädlichen Volumen läßt sich ein hoher Einspritzdruck erzielen.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage, on the one hand, of being extremely flat like the known double-acting valve and, on the other hand, of offering the advantages of a two-valve arrangement, namely the sufficiently precise setting of the opening pressure and the clean closing and opening of the valves both in the funding and in the relief phase. Due to the design, extremely small dead spaces and the associated extremely low harmful volume, a high injection pressure can be achieved.

Zeichnungdrawing

Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

  • Fig. 1 ausschnittweise einen Längsschnitt eines Pumpengehäuses mit eingesetzter Ventilanordnung einer Kraftstoffeinspritzpumpe,
  • Fig.2 einen Querschnitt einer Ventilschließfeder eines Druckventils bzw. eines Ventilschließgliedes eines Entlastungsventils der Ventilanordnung in Fig. 1.
The invention is explained in more detail in the following description with reference to an embodiment shown in the drawing. Show it:
  • 1 shows a detail of a longitudinal section of a pump housing with an inserted valve arrangement of a fuel injection pump,
  • 2 shows a cross section of a valve closing spring of a pressure valve or a valve closing member of a relief valve of the valve arrangement in FIG. 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die in Fig. 1 ausschnittweise im Längsschnitt zu sehende Kraftstoffeinspritzpumpe für eine Brennkraftmaschine weist ein Pumpengehäuse 10 mit einer Bohrung 11 auf, in welchereinerseits eine Zylinderbüchse 12, in welcher ein Pumpenkolben 13 axial verschieblich geführt ist, und andererseits eine Zweiventilanordnung, im folgenden Gleichdruckventil 14 genannt, eingesetzt ist. Pumpenkolben 13, Zylinderbüchse 12 und die untere Stirnseite 15 des Gleichdruckventils 14 begrenzen einen Pumpenarbeitsraum 16 der Kraftstoffeinspritzpumpe. In der gegenüberliegenden Stirnseite des Gleichdruckventils 12 mündet ein Anschlußkanal 17 für eine zu einer nicht dargestellten Einspritzdüse führende Druckleitung.The fuel injection pump for an internal combustion engine, which can be seen in detail in longitudinal section in FIG. 1, has a pump housing 10 with a bore 11 in which, on the one hand, a cylinder liner 12, in which a pump piston 13 is guided axially displaceably, and on the other hand, a two-valve arrangement, hereinafter referred to as a constant pressure valve 14 , is used. Pump piston 13, cylinder liner 12 and the lower end face 15 of the constant pressure valve 14 delimit a pump working space 16 of the fuel injection pump. In the opposite end of the constant pressure valve 12, a connection channel 17 opens for a pressure line leading to an injection nozzle, not shown.

Das Gleichdruckventil 14 weist in räumlicher Hintereinanderordnung ein in Kraftstofförderrichtung, also vom Pumpenarbeitsraum 16 zum Anschlußkanal 17 hin, öffnendes Druckventil 18 und ein in Gegenrichtung öffnendes Entlastungsventil 19 auf. Das Druckventil 18 steuert den Kraftstoffdurchgang zur Einspritzdüse, während das Entlastungsventil 19 der Verhinderung von sogenanntem Nachspritzen der Einspritzdüse sowie der Vermeidung von Kavitationsschäden infolge von Druckwellen dient, die sich beim Schließen der Einspritzdüse ausbilden und bei abgeschlossener Druckleitung mehrfach reflektiert werden.The constant pressure valve 14 has, in spatial succession, a pressure valve 18 which opens in the fuel delivery direction, that is to say from the pump working chamber 16 to the connecting duct 17, and a relief valve 19 which opens in the opposite direction. The pressure valve 18 controls the K raftstoffdurchgang to the injection nozzle, while the relief valve is necessary to prevent so-called afterdrip the injection nozzle and the avoidance of cavitation damage due to pressure waves 19, which develop during the closing of the injector and be reflected several times at closed discharge line.

Das Druckventil 18 ist als Platten- oder Tellersitzventil ausgebildet. Es weist einen Ventilsitzkörper 20, eine als Ringscheibe ausgebildete Ventilplatte 21 und eine flachkonische scheibenartige Ventilschließfeder 22 mit zentralem Durchlaß 24 auf. Die Ventilschließfeder 22 ist hier als Tellerfeder ausgebildet (Fig. 2).The pressure valve 18 is designed as a plate or plate seat valve. It has a valve seat body 20, a valve plate 21 designed as an annular disk and a flat-conical disk-like valve closing spring 22 with a central passage 24. The valve closing spring 22 is designed here as a plate spring (FIG. 2).

Der Ventilsitzkörper 20 weist mehrere im Radialabstand von der Ventilachse angeordnete und in Umfangsrichtung versetzte Durchgangsbohrungen 25 auf, die einerseits zum Pumpenarbeitsraum 16 hin offen sind und andererseits von der Ventilplatte 21 abdeckbar sind. Die Ventilschließfeder 22 liegt im Bereich ihres Durchlasses 24 auf der Ventilplatte 21 auf und preßt sich im Umgebungsbereich ihres Außenumfangs an einen Ventilsitz- 26 auf der Stirnseite 27 eines Anschlußstückes 28 auf, wodurch die Ventilplatte 21 auf den Ventilsitzkörper 20 aufgedrückt wird. Das Anschlußstück 28 trägt den zentralen Anschlußkanal 17, dessen Mündungsöffnung in der-Stirnseite 27 im wesentlichen mit dem Durchlaß 24 der Ventilschließfeder 22 und der Ringöffnung 29 der als Ringscheibe ausgebildeten Ventilplatte 21 fluchtet. Durch diese konstruktive Gestaltung bildet die Ventilschließfeder 22 des Druckventils 18 zugleich das Ventilschließ- bzw. -öffnungsglied des Entlastungsventils 19.The valve seat body 20 has a plurality of through bores 25 which are arranged at a radial distance from the valve axis and offset in the circumferential direction, which are open to the pump working chamber 16 on the one hand and can be covered by the valve plate 21 on the other hand. The valve closing spring 22 lies in the region of its passage 24 on the valve plate 21 and presses against a valve seat 26 on the end face 27 of a connecting piece 28 in the vicinity of its outer periphery, as a result of which the valve plate 21 is pressed onto the valve seat body 20. The connection piece 28 carries the central connection channel 17, the opening of which in the front face 27 is essentially aligned with the passage 24 of the valve closing spring 22 and the ring opening 29 of the valve plate 21 designed as an annular disk. Due to this design, the valve closing spring 22 of the pressure valve 18 also forms the valve closing or opening member of the relief valve 19.

Zwischen dem Ventilsitzkörper 20 und dem Anschlußstück 28 ist ein Distanzring 30 angeordnet, in dessen Ringöffnung 31 die Ventilplatte 21 zentriert ist. In der Innenringwandung 32 des Distanzrings 30 ist eine Axialnut 33 angeordnet, die in flüssigkeitsleitender Verbindung mit einer Radialnut 34 steht,die in der zugleich der Ventilsitz bildenden Stirnseite 35 des Ventilsitzkörpers 20 angeordnet ist und in einer der Durchgangsbohrungen 2 mündet. Diese Radialnut 34 wirkt in der Entlastungsphase, also bei geöffnetem Entlastungsventil 19, als Rückströmdrossel für den Kraftstoff aus dem Anschlußkanal 17 zu dem Pumpenarbeitsraum 16. Der Distanzring 30 kann sowohl mit dem Anschlußstück 28 als auch mit dem Ventilsitzkörper 20 einstückig ausgeführt sein, wird aber aus fertigungstechnischen Gründen bevorzugt als Einzelteil ausgeführt.Between the valve seat body 20 and the connector 28, a spacer ring 30 is arranged, in the ring opening 31, the valve plate 21 is centered. In the inner ring wall 32 of the spacer ring 30, an axial groove 33 is arranged, which is in liquid-conducting connection with a radial groove 34, which at the same time the End face 35 of the valve seat body 20 forming the valve seat is arranged and opens into one of the through bores 2. This radial groove 34 acts in the relief phase, that is to say when the relief valve 19 is open, as a backflow throttle for the fuel from the connection channel 17 to the pump work space 16. The spacer ring 30 can be designed in one piece with both the connection piece 28 and the valve seat body 20, but is made from manufacturing reasons preferably carried out as a single part.

Das Anschlußstück 28, der Distanzring 30 und der Ventilsitzkörper 20 sind außen von einer Hochdruckdichtung 36 umgeben, die auf die freie Stirnseite 15 des Ventilsitzkörpers. 20 mit einem Umbördelungsrand 37 übergreift und durch Sicken 38 mit dem Anschlußstück 28 formschlüssig verbunden ist.The connector 28, the spacer ring 30 and the valve seat body 20 are surrounded on the outside by a high-pressure seal 36, which on the free end face 15 of the valve seat body. 20 overlaps with a flange 37 and is positively connected to the connector 28 by beads 38.

Die Funktionsweise des Gleichdruckventils 14 ist wie folgt:

  • Beim Förderhub wird mit Erreichen des Öffnungsdrucks die Ventilplatte 21 von ihrem Ventilsitz 35 auf dem Ventilsitzkörper 20 entgegen der Wirkung der Ventilschließfeder 22 abgehoben, so daß nunmehr eine Verbindung vom Pumpenarbeitsraum 16 über die Durchgangsbohrungen 25, die Ringöffnung 29 in der Ventilplatte 21 und den zentralen Durchlaß 24 der Ventilschließfeder 22 zum Anschlußkanal 17 besteht. Damit fließt Kraftstoff vom Pumpenarbeitsraum 16 zu der nicht dargestellten Einspritzdüse. Sinkt der Druck unter den Öffnungsdruck des Druckventils 18 ab, so setzt die Ventilplatte 21 wieder auf den Ventilsitzkörper 20 auf und der Kraftstoffluß ist unterbrochen.
The mode of operation of the constant pressure valve 14 is as follows:
  • During the delivery stroke, when the opening pressure is reached, the valve plate 21 is lifted from its valve seat 35 on the valve seat body 20 against the action of the valve closing spring 22, so that now a connection from the pump working space 16 via the through holes 25, the ring opening 29 in the valve plate 21 and the central passage 24 of the valve closing spring 22 to the connecting channel 17. Fuel therefore flows from the pump work chamber 16 to the injector, not shown. If the pressure drops below the opening pressure of the pressure valve 18, the valve plate 21 rests on the valve seat body 20 and the fuel flow is interrupted.

Sofern der Druck in dem Anschlußkanal 17 jedoch höher ist, als die Federkraft der nunmehr als Ventilglied für das Entlastungsventil 19 wirksamen Tellerfeder 23, so hebt diese am Außenumfang von ihrem Ventilsitz 26 am Anschlußstück 28 ab, so daß nunmehr Kraftstoff in Gegenrichtung aus dem Anschlußkanal 17 über die Axialnut 33, die als Rückströmdrossel wirkende Radialnut 34 und die eine Durchgangsbohrung 25 zum Pumpenarbeitsraum 16 fließen kann. Das Entlastungsventil 19 bestimmt somit den in der Druckleitung zur Einspritzdüse verbleibenden Standdruck,und die Rückströmdrossel 34 dämpft in gewünschter Weise den Entlastungsvorgang.If, however, the pressure in the connection channel 17 is higher than the spring force of the plate spring 23, which is now effective as a valve member for the relief valve 19, this springs on the outer circumference of its valve seat 26 on the connection piece 28, so that fuel now flows in the opposite direction from the connection channel 17 Via the axial groove 33, the radial groove 34 acting as a backflow throttle and a through hole 25 can flow to the pump working space 16. The relief valve 19 thus determines the standing pressure remaining in the pressure line to the injection nozzle, and the backflow throttle 34 dampens the relief process in the desired manner.

Claims (5)

1. Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit zwei zwischen einem in einem Pumpengehäuse angeordneten Pumpenarbeitsraum und einer zu einer Einspritzdüse führenden Druckleitung eingeschalteten Ventilen, von denen das eine ein in Kraftstofförderrichtung öffnendes Druckventil und das andere ein in Gegenrichtung öffnendes Entlastungsventil ist, dadurch gekennzeich- net, daß die beiden Ventile (18,19) räumlich hintereinander angeordnet sind, daß das Druckventil (18) als Platten- oder Tellersitzventil mit einem Ventilsitzkörper (20), einer Ventilplatte (21) und einer die Ventilplatte (21) auf den Ventilsitz aufdrückenden, flachkonischen scheibenartigen Ventilschließfeder(22)ausgebildet ist und daß die Ventilschließfeder(22)zugleich das Ventilglied des Entlastungsventils (19) bildet.1. Fuel injection pump for internal combustion engines with two valves connected between a pump work chamber arranged in a pump housing and a pressure line leading to an injection nozzle, one of which is a pressure valve opening in the fuel delivery direction and the other a relief valve opening in the opposite direction, characterized in that the two valves (18, 19) are arranged spatially one behind the other, that the pressure valve (18) as a plate or disc seat valve with a valve seat body (20), a valve plate (21) and a flat-conical disc-like valve closing spring pressing the valve plate (21) onto the valve seat (22) is formed and that the valve closing spring (22) also forms the valve member of the relief valve (19). 2. Einspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilsitzkörper (20) des Druckventils '(18) im Radialabstand von der Ventilachse angeordnete und in Umfangsrichtung versetzte Durchgangsbohrungen (25), die einerseits zum Pumpenarbeitsraum (16) hin offen und andererseits von der Ventilplatte (21) abdeckbar sind, und an seiner ventilsitz- . seitigen Stirnseite (35) eine von einer Durchgangsbohrung (25) ausgehende, bis außerhalb des Abdeckbereichs der Ventilplatte (21) reichende, als Rückströmdrossel wirkende Radialnut (34) aufweist, daß die Ventilplatte (21) als Ringscheibe ausgebildet ist und daß die Ventilschließfeder (22), die vorzugsweise als Tellerfeder ausgebildet ist, einen zentralen Durchlaß (24) aufweist und im Umgebungsbereich ihres Außenumfangs an einem Ventilsitz (26) auf der Stirnseite (27) eines Anschlußstückes (28) anliegt, das einen mit der Druckleitung in Verbindung stehenden zentralen Anschlußkanal (17) aufweist, dessen Mündungsöffnung im wesentlichen mit dem Durchlaß (24) der Ventilschließfeder (22) und der Ringöffnung (29) der Ventilplatte. (21) fluchtet.2. Injection pump according to claim 1, characterized in that the valve seat body (20) of the pressure valve '(18) is arranged at a radial distance from the valve axis and in Through holes (25) offset in the circumferential direction, which on the one hand are open to the pump work chamber (16) and on the other hand can be covered by the valve plate (21), and on its valve seat. End face (35) has a radial groove (34) extending from a through hole (25) and extending outside the cover area of the valve plate (21), acting as a backflow throttle, that the valve plate (21) is designed as an annular disc and that the valve closing spring (22 ), which is preferably designed as a plate spring, has a central passage (24) and bears in the vicinity of its outer circumference on a valve seat (26) on the end face (27) of a connection piece (28) which has a central connection channel connected to the pressure line (17), the opening of the mouth essentially with the passage (24) of the valve closing spring (22) and the ring opening (29) of the valve plate. (21) is aligned. 3. Einspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß zwischen dem Ventilsitzkörper (20) und dem Anschlußstück (28) ein Distanzring (30) angeordnet ist, in dessen Ringöffnung (31) die Ventilplatte (21) zentriert ist, und daß in der Innenringwandung (32) des Distanzrings (30) eine mit der Radialnut (34) im Ventilsitzkörper (20) in Verbindung stehende Axialnut (33) angeordnet ist.3. Injection pump according to claim 2, characterized in that between the valve seat body (20) and the connecting piece (28) a spacer ring (30) is arranged, in the ring opening (31), the valve plate (21) is centered, and that in the inner ring wall (32) of the spacer ring (30) there is an axial groove (33) connected to the radial groove (34) in the valve seat body (20). 4. Einspritzpumpe nach Anspruch 3, dadurch gekennzeichnet, daß Distanzring (30) und Anschlußstück (28) oder Distanzring (30) und Ventilsitzkörper (20) einstückig ausgebildet sind.4. Injection pump according to claim 3, characterized in that the spacer ring (30) and connector (28) or spacer ring (30) and valve seat body (20) are integrally formed. 5. Einspritzpumpe nach Anspruch 3 oder 4, da- durch gekennzeichnet, daß Anschlußstück (28),- Distanzring (30) und Ventilsitzkörper (20) von einer Hochdruckdichtung (36) umgeben sind, die auf die freie Stirnseite (15) des Ventilsitzkörpers (20) mit einem Umbördelungsrand (37) übergreift und durch Sicken (38) mit dem Anschlußstück (28) formschlüssig verbunden ist.5. Injection pump according to claim 3 or 4, characterized in that the connecting piece (28), - spacer ring (30) and valve seat body (20) are surrounded by a high pressure seal (36) which on the free end face (15) of the valve seat body ( 20) overlaps with a flange (37) and is positively connected to the connecting piece (28) by beads (38).
EP84116244A 1984-02-10 1984-12-22 Fuel injection pump for internal combustion engines Withdrawn EP0153491A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8404020U 1984-02-10
DE19848404020 DE8404020U1 (en) 1984-02-10 1984-02-10 Fuel injection pump for internal combustion engines

Publications (1)

Publication Number Publication Date
EP0153491A1 true EP0153491A1 (en) 1985-09-04

Family

ID=6763406

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116244A Withdrawn EP0153491A1 (en) 1984-02-10 1984-12-22 Fuel injection pump for internal combustion engines

Country Status (3)

Country Link
EP (1) EP0153491A1 (en)
JP (1) JPS60145277U (en)
DE (1) DE8404020U1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275522A (en) * 1993-02-26 1994-08-31 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB729763A (en) * 1952-07-21 1955-05-11 Napier & Son Ltd Improvements in surge reducing or pressure reducing valves for the fuel injection apparatus of internal combustion engines
WO1980002180A1 (en) * 1979-04-09 1980-10-16 Caterpillar Tractor Co Safety check valve for unit fuel pump-injector

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1815254A1 (en) * 1968-12-18 1970-08-13 Maschf Augsburg Nuernberg Ag Device for equal pressure relief on fuel injection pump pressure lines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB729763A (en) * 1952-07-21 1955-05-11 Napier & Son Ltd Improvements in surge reducing or pressure reducing valves for the fuel injection apparatus of internal combustion engines
WO1980002180A1 (en) * 1979-04-09 1980-10-16 Caterpillar Tractor Co Safety check valve for unit fuel pump-injector

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275522A (en) * 1993-02-26 1994-08-31 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector
GB2275522B (en) * 1993-02-26 1996-09-18 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector

Also Published As

Publication number Publication date
JPS60145277U (en) 1985-09-26
JPH041338Y2 (en) 1992-01-17
DE8404020U1 (en) 1985-06-13

Similar Documents

Publication Publication Date Title
EP1671031B1 (en) Fluid pump, particularly high-pressure fuel pump
US4577606A (en) Pressure valve assembly for fuel injection pumps
DE4341546A1 (en) Fuel injection device for internal combustion engines
DE4237469A1 (en) Fuel injection device, in particular pump nozzle for internal combustion engines
DE4341545A1 (en) Fuel injection device for internal combustion engines
DE102006051327A1 (en) Fuel injector
EP0900334B1 (en) Pressure valve
EP0925447B1 (en) Radial piston pump for high pressure fuel supply
EP0931219A1 (en) High-pressure fuel pump
DE2656276A1 (en) INJECTION SYSTEM FOR SELF-IGNING COMBUSTION MACHINERY
EP1312796B1 (en) Fuel injection valve
DE3734587A1 (en) Fuel injection nozzle for internal combustion engines
EP0153491A1 (en) Fuel injection pump for internal combustion engines
DE19753162A1 (en) Fuel injection valve for internal combustion engines
DE829682C (en) Injection valve for internal combustion engines
DE827140C (en) Fuel injector
EP0811119B1 (en) Fuel injection valve for internal combustion engines
EP0153490B1 (en) Constant-pressure delivery valve for fuel injection pumps
EP0906506B1 (en) Fuel injection pump for an internal combustion engine
WO1995024552A1 (en) Injection nozzle for internal combustion engines
EP0152619A1 (en) Fuel injection pump for internal combustion engines
DE2930499A1 (en) Fuel injection pump for diesel engine - has annular groove round discharge valve seat to reduce cavitation in fuel
DE840334C (en) Speed-dependent delivery rate control for injection pumps
DE4139907A1 (en) High pressure fuel injection device - has labyrinth seal between pump piston and cylinder liner, or between nozzle pin and housing
DE10121340A1 (en) Common rail injector for internal combustion engine fuel injection system has casing and intermediate plate bounding control chamber implemented in one piece with inlet and outlet choke

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19841222

AK Designated contracting states

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19860724

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19861203

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HAEFELE, WALTER, ING.

Inventor name: SCHWARTZ, REINHARD, DIPL.-ING.