EP0061534A1 - Delivery valve for a fuel injection pump - Google Patents

Delivery valve for a fuel injection pump Download PDF

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Publication number
EP0061534A1
EP0061534A1 EP81110498A EP81110498A EP0061534A1 EP 0061534 A1 EP0061534 A1 EP 0061534A1 EP 81110498 A EP81110498 A EP 81110498A EP 81110498 A EP81110498 A EP 81110498A EP 0061534 A1 EP0061534 A1 EP 0061534A1
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EP
European Patent Office
Prior art keywords
valve
valve body
injection
section
channel
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.)
Ceased
Application number
EP81110498A
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German (de)
French (fr)
Inventor
Helmut Laufer
Karl Zibold
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0061534A1 publication Critical patent/EP0061534A1/en
Ceased legal-status Critical Current

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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
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the invention relates to a pressure valve between a fuel injection pump and an injection valve according to the preamble of the main claim.
  • the known pressure valves the valve bodies of which consist of cones and of guide stems molded onto them, are pressed against their valve seats by means of very strong closing springs. Even small valve body strokes. are sufficient so that large amounts of fuel to be injected can flow through the valve cross sections and around the valve body.
  • the closing springs close these pressure valves very quickly. This is why pressure waves that arise when the injection valves close and travel through injection lines to the pressure valves hit the valve bodies when they are already firmly seated on their valve seats.
  • This has the disadvantages that the pressure waves in the pressure valves are reflected very hard and then move back into the injection valves and open them again. The opening can be done several times and causes undesirable amounts of pollutants when burning the fuel and increased fuel consumption.
  • the valve body because it has little mass in relation to its cross section and fills the channel except for a narrow throttle cross section, is displaced so far during an injection process against the closing spring that between the valve seat and the Valve body in the channel finds a volume that substantially corresponds to the fuel volume delivered by the injection pump into the pressure valve.
  • the valve body is thus moved like a movable wall between the injection pump and the injection valve.
  • the closing spring moves the light valve body in the direction of its valve seat. Because of the throttle cross-section and the coordinated force of the closing spring, the displacement is slow.
  • the pressure valve 2 is screwed to an injection pump 3.
  • the pressure valve 2 has a valve seat 4, a movable valve body 5, a closing spring 6 and a housing 7.
  • the housing 7 is screwed into the injection pump by means of a thread 8. Starting from its free end 9, the housing 7 has a channel 10. In the channel 10, the valve body 5 can be displaced in the longitudinal direction of the housing 7. An abutment 11 for the closing spring 6 connects to the channel.
  • the closing spring 6 is arranged between this abutment 11 and the valve body 5. With its end 9, the housing 7 presses against the valve seat 4, which has the shape of a perforated disc.
  • the valve seat 4 is sealed off from the housing 7 by means of a seal 12.
  • a channel 13 leads to the valve seat 4 and comes from a pump chamber (not shown).
  • the valve body 5 has a valve surface 14 which, together with the side 15 of the valve seat 4 facing it, forms a sealing pairing.
  • the diameter of the channel 10 and that of the valve body 5 are coordinated with one another in such a way that a throttle cross section 16 remains between them.
  • the length of the channel 6 is selected so that the valve body 5 has a displacement path which, multiplied by the diameter of the channel 10, results in a volume which is able to accommodate the largest possible fuel volume which is delivered by the injection pump 3 into the pressure valve 2 .
  • Subsequent to the abutment 11 is in the housing 7 a channel 17 drilled in, which leads to an injection line, not shown, and an injection valve, not shown.
  • the valve body 5 is designed essentially in the manner of a round disk, onto which the valve surface 14, which has the shape of a circular ring, is molded in the form of a rib. Towards the channel 17, the valve body 5 has a pin 18 which is surrounded by the closing spring 6. The drawn position of the valve body 5 is its rest or sealing position. When fuel is pressed against the pressure valve 2 by the injection pump, the valve body 5 moves in the direction of the channel 17 against the force of the closing spring 6. Fuel that is located in the area of the closing spring-6 is pressed into the channel 17. This fuel drives the fuel that is located in this channel 17 and the subsequent injection line to the injection nozzle.
  • the injection nozzle When a sufficiently high pressure is reached at the injection nozzle, it opens and fuel is injected into a combustion chamber of an internal combustion engine, not shown.
  • the injection pump 3 As soon as the injection pump 3 has pumped a preselected amount of fuel into the pressure valve 2, the injection valve begins to close and the closing spring 6 begins to move the valve body 5 in the direction of the valve seat 4.
  • the force of the closing spring 6, the cross section of the channel 10 and the throttle cross section 16 are coordinated with one another in such a way that the valve body 5 moves in the direction of the valve seat, a pressure wave which is triggered by the closing of the injection valve and through the injection line and the channel 17 to the Vent: .lSystem 5 wanders, reaches this before he puts on the valve seat 4.
  • the pressure wave thus hits the valve body 5 at a point in time at which the poch is so far apart from the valve seat 4 that the pressure wave cannot strike the valve body 5 against the valve seat 4. Therefore, the pressure wave cannot find one Resistance that could trigger a hard reflection of the pressure wave. So that the valve body 5, which has not yet reached the valve seat 4, in turn now acts as little as possible as a reflector, it is made as thin and light as possible and consists of a material with a specifically low weight. After the pressure wave disappears, the closing spring 6 pushes the valve body 5 further in the direction of the valve seat 4. The force of the closing spring 6 overcomes damping forces which occur when fuel in the channel 10 flows through the throttle cross section 16. The valve body 5 sits tightly on the valve seat 4 before the start of the next injection process.

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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

The delivery valve (2) is installed between an injection pump (3) and an injection valve and has a disc-like valve body (5) which is pressed against a valve seat (4) by a closing spring (6) and which forms a throttle cross-section (16) with a channel (10). The dimensions of the valve body (5), the throttle cross-section (16) and the closing force of the closing spring (6) are matched to one another in such a manner that after an injection process has finished, the valve body (5) moves with delay in the direction of the valve seat (4). This prevents a hard reflection of the pressure wave which would lead to the injection valve opening again. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Druckventil zwischen einer Brennstoffeinspritzpumpe und einem Einspritzventil nach der Gattung des Hauptanspruchs. Die bekannten Druckventile, deren Ventilkörper aus Kegeln und aus an diese angeformten Führungsstielen bestehen, werden mittels sehr starker Schließfedern gegen ihre Ventilsitze gedrückt. Schon kleine Ventilkörperhübe. genügen, damit auch große einzuspritzende Brennstoffmengen durch die Ventilquerschnitte und um die Ventilkörper herumströmen können. Bei Beendigung der Einspritzvorgänge schließen die Schließfedern diese Druckventile sehr schnell. Deshalb treffen Druckwellen, die beim Schließen der Einspritzventile entstehen und durch Einspritzleitungen zu den Druckventilen wandern, auf die Ventilkörper, wenn sie schon fest auf ihren Ventilsitzen ruhen. Dies hat die Nachteile, daß die Druckwellen in den Druckventilen sehr hart reflektiert werden und nach'.dem zurückwandern in die Einspritzventile diese nochmals öffnen. Das Öffnen kann mehrmals erfolgen und verursacht unerwünschte Schadstoffmengen bei der Verbrennung des Brennstoffs und erhöhten Brennstoffverbrauch.The invention relates to a pressure valve between a fuel injection pump and an injection valve according to the preamble of the main claim. The known pressure valves, the valve bodies of which consist of cones and of guide stems molded onto them, are pressed against their valve seats by means of very strong closing springs. Even small valve body strokes. are sufficient so that large amounts of fuel to be injected can flow through the valve cross sections and around the valve body. When the injection processes are completed, the closing springs close these pressure valves very quickly. This is why pressure waves that arise when the injection valves close and travel through injection lines to the pressure valves hit the valve bodies when they are already firmly seated on their valve seats. This has the disadvantages that the pressure waves in the pressure valves are reflected very hard and then move back into the injection valves and open them again. The opening can be done several times and causes undesirable amounts of pollutants when burning the fuel and increased fuel consumption.

Vorteile der ErfindungAdvantages of the invention

Bei dem Druckventil mit den kennzeichnenden Merkmalen nach dem Hauptanspruch wird der Ventilkörper, weil er im Verhältnis zu seinem Querschnitt wenig Masse hat und den Kanal bis auf einen engen Drosselquerschnitt ausfüllt, bei einem Einspritzvorgang gegen die Schließfeder so weit verschoben, daß zwischen dem Ventilsitz und dem Ventilkörper in dem Kanal ein Volumen, das im wesentlichen mit dem von der Einspritzpumpe in das Druckventil geförderten Brennstoffvolumen übereinstimmt, Raum findet. Der Ventilkörper wird also wie eine bewegliche Wand zwischen der Einspritzpumpe und dem Einspritzventil verschoben. Wenn die Einspritzpumpe ein vorgewähltes Brennstoffvolumen in das Druckventil gefördert hat, verschiebt die Schließfeder den leichten Ventilkörper in Richtung seines Ventilsitzes. Wegen des Drosselquerschnitts und der abgestimmten Kraft der Schließfeder geht die Verschiebung langsam vor sich. Dies bewirkt, daß eine Druckwelle, die durch das Schließen des Einspritzventils erzeugt wird, auf den Ventilkörper trifft, so lange er noch einen Abstand zu dem Ventilsitz hat. Dies hat den Vorteil, daß beim Eintreffen der Druckwelle der Ventilsitz noch kein Widerlager für den Ventilkörper bildet und daß der Ventilkörper aufgrund seiner geringen Masse nur noch eine sehr schwache, unbedeutende Reflexion verursachen kann. Durch die Abstimmung der Masse des Ventilkörpers, der Kraft der Schließfeder und des Drosselquerschnitts aufeinander, setzt sich der Ventilkörper noch vor Beginn des nächsten Einspritzvorgangs auf seinen Ventilsitz.In the pressure valve with the characterizing features according to the main claim, the valve body, because it has little mass in relation to its cross section and fills the channel except for a narrow throttle cross section, is displaced so far during an injection process against the closing spring that between the valve seat and the Valve body in the channel finds a volume that substantially corresponds to the fuel volume delivered by the injection pump into the pressure valve. The valve body is thus moved like a movable wall between the injection pump and the injection valve. When the injection pump has delivered a preselected fuel volume into the pressure valve, the closing spring moves the light valve body in the direction of its valve seat. Because of the throttle cross-section and the coordinated force of the closing spring, the displacement is slow. This causes a pressure wave generated by the closing of the injection valve to strike the valve body while it is still a distance from the valve seat. This has the advantage that when the pressure wave arrives, the valve seat does not yet form an abutment for the valve body and that the valve body can only cause a very weak, insignificant reflection due to its low mass. By coordinating the mass of the valve body, the force of the closing spring and the throttle cross-section, the valve body sits on its valve seat before the next injection process begins.

Die Maßnahmen nach den Ansprüchen 2 und 3 bewirken, daß Reflexionen von Druckwellen, die an dem sich.bewegenden Ventilkörper auftreten, vermindert werden.The measures according to claims 2 and 3 have the effect that reflections of pressure waves which occur on the moving valve body are reduced.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is shown in the drawing and explained in more detail in the following description.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das Druckventil 2 ist mit einer Einspritzpumpe 3 verschraubt. Das Druckventil 2 hat einen Ventilsitz 4, einen beweglichen Ventilkörper 5, eine Schließfeder 6 und ein Gehäuse 7. Das Gehäuse 7 ist mittels eines Gewindes 8 in die Einspritzpumpe geschraubt. Von seinem freien Ende 9 ausgehend hat das Gehäuse 7 einen Kanal 10. In dem Kanal 10 ist der Ventilkörper 5 in Längsrichtung des Gehäuses 7 verschiebbar. An den Kanal schließt sich ein Widerlager 11 für die Schließfeder 6 an. Die Schließfeder 6 ist zwischen diesem Widerlager 11 und dem Ventilkörper 5 angeordnet. Mit seinem Ende 9 drückt das Gehäuse 7 gegen den Ventilsitz 4, der die Form einer gelochten Scheibe hat. Zu dem Gehäuse 7 hin ist der Ventilsitz 4 mittels einer Dichtung 12 abgedichtet. Zu dem Ventilsitz 4 führt ein Kanal 13, der von einem nicht dargestellten Pumpenraumlkommt.The pressure valve 2 is screwed to an injection pump 3. The pressure valve 2 has a valve seat 4, a movable valve body 5, a closing spring 6 and a housing 7. The housing 7 is screwed into the injection pump by means of a thread 8. Starting from its free end 9, the housing 7 has a channel 10. In the channel 10, the valve body 5 can be displaced in the longitudinal direction of the housing 7. An abutment 11 for the closing spring 6 connects to the channel. The closing spring 6 is arranged between this abutment 11 and the valve body 5. With its end 9, the housing 7 presses against the valve seat 4, which has the shape of a perforated disc. The valve seat 4 is sealed off from the housing 7 by means of a seal 12. A channel 13 leads to the valve seat 4 and comes from a pump chamber (not shown).

Der Ventilkörper 5 hat eine Ventilfläche 14, die zusammen mit der ihm zugekehrten Seite 15 des Ventilsitzes 4 eine dichtende Paarung bildet. Der Durchmesser des Kanals 10 und der des Ventilkörpers 5 sind derart aufeinander abgestimmt, daß zwischen ihnen ein Drosselquerschnitt 16 verbleibt. Die Länge des Kanals 6 ist so gewählt, daß dem Ventilkörper 5 ein Verschiebeweg zur Verfügung steht, der mit dem Durchmesser des Kanals 10 multipliziert ein Volumen ergibt, das das größtmögliche Brennstoffvolumen, das von der Einspritzpumpe 3 in das Druckventil 2 gefördert wird, aufzunehmen vermag. Anschließend an das Widerlager 11 ist in das Gehäuse 7 ein Kanal 17 eingebohrt, der zu einer nicht dargestellten Einspritzleitung und einem nicht dargestellten Einspritzventil führt.The valve body 5 has a valve surface 14 which, together with the side 15 of the valve seat 4 facing it, forms a sealing pairing. The diameter of the channel 10 and that of the valve body 5 are coordinated with one another in such a way that a throttle cross section 16 remains between them. The length of the channel 6 is selected so that the valve body 5 has a displacement path which, multiplied by the diameter of the channel 10, results in a volume which is able to accommodate the largest possible fuel volume which is delivered by the injection pump 3 into the pressure valve 2 . Subsequent to the abutment 11 is in the housing 7 a channel 17 drilled in, which leads to an injection line, not shown, and an injection valve, not shown.

Der Ventilkörper 5 ist im wesentlichen nach Art einer runden Scheibe gestaltet, an die die Ventilfläche 14, die die Form eines Kreisringes hat, in Form einer Rippe angeformt ist. Zu dem Kanal 17 hin hat der Ventilkörper 5 einen Zapfen 18, der von der Schließfeder 6 umgeben wird. Die gezeichnete Stellung des Ventilkörpers 5 ist seine Ruhe- bzw. Abdichtstellung. Wenn von der Einspritzpumpe Brennstoff gegen das Druckventil 2 gedrückt wird, verschiebt sich der Ventilkörper 5 in Richtung des Kanals 17 gegen die Kraft der Schließfeder 6. Dadurch wird Brennstoff, der sich im Bereich der Schließfeder-6 befindet, in den Kanal 17 gedrückt. Dieser Brennstoff treibt denjenigen Brennstoff, der sich in diesem Kanal 17 und der anschließenden Einspritzleitung befindet, zu der Einspritzdüse. Wenn an der Einspritzdüse ein genügend hoher Druck erreicht ist, öffnet sie sich und Brennstoff spritzt in einen Brennraum einer nicht dargestellten Brennkraftmaschine. Sobald die Einspritzpumpe 3 eine vorgewählte Brennstoffmenge in das Druckventil 2 gepumpt hat, beginnt sich das Einspritzventil zu schließen und die Schließfeder 6 beginnt den Ventilkörper 5 in Richtung des Ventilsitzes 4 zu verschieben. Die Kraft der Schließfeder 6, der Querschnitt des Kanals 10 und der Drosselquerschnitt 16 sind so aufeinander abgestimmt, daß sich der Ventilköpper 5 verzöger in Richtung des Ventilsitzes bewegt eine Druckwelle, die durch das Schließen des Einspritzventils ausgelöst wird und durch die Einspritzleitung und den Kanal 17 zu dem Vent:.lkörper 5 wandert, diesen erreicht, bevor er sich an den Ventilsitz 4 anlegt. Die Druckwelle trifft also zu einem Zeitpunkt auf den Ventilkörper 5, an dem dieser poch einen so großen Abstand zu dem Ventilsitz 4 hat, daß die Druckwelle den Ventilkörper 5 nicht gegen den Ventilsitz 4 schlagen kann. Deshalb findet die Druckwelle keinen Widerstand vor, der eine harte Reflexion der Druckwelle auslösen könnte. Damit der Ventilkörper 5, der noch nicht an dem Ventilsitz 4 angelangt ist, nun seinerseits möglichst wenig als Reflektor wirkt, ist er möglichst dünn und leicht ausgebildet und besteht aus einem Werkstoff mit spezifisch geringem Gewicht. Nach dem Verschwinden der Druckwelle schiebt die Schließfeder 6 den Ventilkörper 5 weiter in Richtung des Ventilsitzes 4. Die Kraft der Schließfeder 6 überwindet dabei Dämpfungskräfte die beim Durchströmen von in dem Kanal 10 befindlichen Brennstoff durch den Drosselquerschnitt 16 auftreten. Der Ventilkörper 5 setzt sich noch vor Beginn des nächsten Einspritzvorganges dicht auf den Ventilsitz 4 auf.The valve body 5 is designed essentially in the manner of a round disk, onto which the valve surface 14, which has the shape of a circular ring, is molded in the form of a rib. Towards the channel 17, the valve body 5 has a pin 18 which is surrounded by the closing spring 6. The drawn position of the valve body 5 is its rest or sealing position. When fuel is pressed against the pressure valve 2 by the injection pump, the valve body 5 moves in the direction of the channel 17 against the force of the closing spring 6. Fuel that is located in the area of the closing spring-6 is pressed into the channel 17. This fuel drives the fuel that is located in this channel 17 and the subsequent injection line to the injection nozzle. When a sufficiently high pressure is reached at the injection nozzle, it opens and fuel is injected into a combustion chamber of an internal combustion engine, not shown. As soon as the injection pump 3 has pumped a preselected amount of fuel into the pressure valve 2, the injection valve begins to close and the closing spring 6 begins to move the valve body 5 in the direction of the valve seat 4. The force of the closing spring 6, the cross section of the channel 10 and the throttle cross section 16 are coordinated with one another in such a way that the valve body 5 moves in the direction of the valve seat, a pressure wave which is triggered by the closing of the injection valve and through the injection line and the channel 17 to the Vent: .lkörper 5 wanders, reaches this before he puts on the valve seat 4. The pressure wave thus hits the valve body 5 at a point in time at which the poch is so far apart from the valve seat 4 that the pressure wave cannot strike the valve body 5 against the valve seat 4. Therefore, the pressure wave cannot find one Resistance that could trigger a hard reflection of the pressure wave. So that the valve body 5, which has not yet reached the valve seat 4, in turn now acts as little as possible as a reflector, it is made as thin and light as possible and consists of a material with a specifically low weight. After the pressure wave disappears, the closing spring 6 pushes the valve body 5 further in the direction of the valve seat 4. The force of the closing spring 6 overcomes damping forces which occur when fuel in the channel 10 flows through the throttle cross section 16. The valve body 5 sits tightly on the valve seat 4 before the start of the next injection process.

Claims (3)

1. Druckventil für eine Brennstoffeinspritzpumpe mit einem Ventilsitz, mit einem in Richtung einer anzuschließenden Einspritzdüse sich an den Ventilsitz anschließenden Kanal, mit einem in dem Kanal verschiebbaren Ventilkörper und mit einer Schließfeder und mit einem Durchgangsquerschnitt zwischen dem Querschnitt des Kanals und dem Querschnitt des Ventilkörpers, dadurch gekennzeichnet, daß der Ventil-körper (5) im wesentlichen scheibenförmig ausgebildet ist, daß der Durchgangsquerschnitt als Drosselquerschnitt (16) gestaltet ist, daß die Schließfeder (6) eine solche Schließkraft hat, daß im Zusammenwirken mit dem Drosselquerschnitt (16) der Ventilkörper (5) nach Beeendigung eines Einspritzvorgangs verzögert, aber noch vor Beginn der nächsten Einspritzung auf den Ventilsitz (4) trifft, und daß für den Ventilkörper (5) in dem Kanal (10) ein Verschiebeweg vorhanden ist mit einer Länge, die mit dem Querschnitt des Kanals (10) multipliziert ein Volumen ergibt, das wenigstens so groß ist wie das bei einem Einspritzhub der Einspritzpumpe (3) in das Druckventil (2) geförderte maximale Brennstoffvolumen..1. Pressure valve for a fuel injection pump with a valve seat, with a channel adjoining the valve seat in the direction of an injection nozzle, with a valve body displaceable in the channel and with a closing spring and with a passage cross section between the cross section of the channel and the cross section of the valve body, characterized in that the valve body (5) is substantially disc-shaped, that the passage cross-section is designed as a throttle cross-section (16), that the closing spring (6) has such a closing force that, in cooperation with the throttle cross-section (16), the valve body (5) delayed after completion of an injection process, but still hits the valve seat (4) before the start of the next injection, and that for the valve body (5) in the channel (10) there is a displacement path with a length which corresponds to the cross section of the channel (10) multiplied results in a volume that is at least as large as that with an injection stroke of the injection pump (3) into the pressure valve (2) delivered maximum fuel volume .. 2. Druckventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilkörper (5) wenigstens zonenweise dünn ausgebildet ist.2. Pressure valve according to claim 1, characterized in that the valve body (5) is at least zone thin. 3. Druckventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Ventilkörper (5) aus einem Werkstoff mit geringem spezifischem Gewichttbesteht.3. Pressure valve according to claim 1 or 2, characterized in that the valve body (5) consists of a material with a low specific weight.
EP81110498A 1981-03-27 1981-12-16 Delivery valve for a fuel injection pump Ceased EP0061534A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813112100 DE3112100A1 (en) 1981-03-27 1981-03-27 "PRESSURE VALVE FOR A FUEL INJECTION PUMP"
DE3112100 1981-03-27

Publications (1)

Publication Number Publication Date
EP0061534A1 true EP0061534A1 (en) 1982-10-06

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Application Number Title Priority Date Filing Date
EP81110498A Ceased EP0061534A1 (en) 1981-03-27 1981-12-16 Delivery valve for a fuel injection pump

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EP (1) EP0061534A1 (en)
JP (1) JPS57171071A (en)
BR (1) BR8201722A (en)
DE (1) DE3112100A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0147591A2 (en) * 1983-12-12 1985-07-10 Robert Bosch Gmbh Delivery valve for fuel injection pumps
US5287838A (en) * 1993-02-26 1994-02-22 Caterpillar Inc. Compact reverse flow check valve assembly for a unit fluid pump-injector
US5715795A (en) * 1995-09-25 1998-02-10 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
WO2005078273A1 (en) * 2004-02-11 2005-08-25 Robert Bosch Gmbh High pressure pump, in particular for a fuel injection device in an internal combustion engine

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Publication number Priority date Publication date Assignee Title
DE112011105549T5 (en) * 2011-08-24 2014-05-15 Toyota Jidosha Kabushiki Kaisha Fluid control device and fuel supply system
CN110552827B (en) * 2018-06-04 2022-11-11 罗伯特·博世有限公司 Oil inlet valve for high-pressure oil pump and corresponding high-pressure oil pump

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CH305822A (en) * 1950-11-17 1955-03-15 Nat Res Dev Fuel injection device with an injection nozzle and a piston pump.
DE1171204B (en) * 1962-05-11 1964-05-27 Bosch Gmbh Robert Fuel injector
DE2028321A1 (en) * 1969-06-09 1970-12-17 Mitsubishi Jukogvo K.K., Tokio Fuel injection pump
DE2547783A1 (en) * 1974-12-19 1976-06-24 Friedmann & Maier Ag FUEL INJECTION PUMP

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DE630230C (en) * 1934-02-13 1936-05-23 Humboldt Deutzmotoren A G Injection device for internal combustion engines
DE702425C (en) * 1934-11-01 1941-02-07 Deckel Friedrich Return valve, especially for injection pumps of internal combustion engines
CH186053A (en) * 1934-12-05 1936-08-31 Limited Belfrost Diesels Fuel injection pump.
US2090688A (en) * 1935-05-14 1937-08-24 Lawrence W Lindberg Fuel supply pump
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Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH305822A (en) * 1950-11-17 1955-03-15 Nat Res Dev Fuel injection device with an injection nozzle and a piston pump.
DE1171204B (en) * 1962-05-11 1964-05-27 Bosch Gmbh Robert Fuel injector
DE2028321A1 (en) * 1969-06-09 1970-12-17 Mitsubishi Jukogvo K.K., Tokio Fuel injection pump
DE2547783A1 (en) * 1974-12-19 1976-06-24 Friedmann & Maier Ag FUEL INJECTION PUMP

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0147591A2 (en) * 1983-12-12 1985-07-10 Robert Bosch Gmbh Delivery valve for fuel injection pumps
EP0147591A3 (en) * 1983-12-12 1986-02-05 Robert Bosch Gmbh Delivery valve for fuel injection pumps
US5287838A (en) * 1993-02-26 1994-02-22 Caterpillar Inc. Compact reverse flow check valve assembly for a unit fluid pump-injector
US5715795A (en) * 1995-09-25 1998-02-10 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
WO2005078273A1 (en) * 2004-02-11 2005-08-25 Robert Bosch Gmbh High pressure pump, in particular for a fuel injection device in an internal combustion engine

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BR8201722A (en) 1983-02-22
DE3112100A1 (en) 1982-10-07
JPS57171071A (en) 1982-10-21

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