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EP0073967A1 - Fuel injection pump for internal-combustion engines - Google Patents

Fuel injection pump for internal-combustion engines Download PDF

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Publication number
EP0073967A1
EP0073967A1 EP19820107462 EP82107462A EP0073967A1 EP 0073967 A1 EP0073967 A1 EP 0073967A1 EP 19820107462 EP19820107462 EP 19820107462 EP 82107462 A EP82107462 A EP 82107462A EP 0073967 A1 EP0073967 A1 EP 0073967A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve closing
closing body
spring
bracket
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Withdrawn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
EP19820107462
Other languages
German (de)
French (fr)
Inventor
Walter Häfele
Bernhard Schenk
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 EP0073967A1 publication Critical patent/EP0073967A1/en
Withdrawn legal-status Critical Current

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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
    • F02M59/44—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve
    • Y10T137/7776—Spring abuts guide for supported valve stem

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of the main claim.
  • injection pumps equipped with a constant pressure relief valve (CH-PS 394 710)
  • the spring of the relief valve is supported by a screw part which is fastened in the sleeve-shaped section of the valve closing body.
  • the disadvantage of this screw connection is that because of a possible loosening, the safe functioning of the injection pump is not always given, because parts of the valve falling into the pump work space can lead to serious damage to the injection pump and consequential damage to the internal combustion engine.
  • the invention is based on the idea of using the hollow cylindrical wall of the valve closing body as an abutment.
  • FIG. 1 shows in sections a fuel injection pump with the constant pressure relief valve according to the invention in an enlarged axial section and
  • FIG. 2 shows a partial view of the valve closing body in the direction of arrow II in FIG. 1.
  • FIG. 1 shows a pressure valve 9 acting as a constant pressure relief valve, the valve carrier 12 of which is fastened in a pump housing 10 with a valve seat ring surface 13 between a cylinder liner 11 and a pressure piece 14.
  • a movable valve closing body 15 is pressed with its valve closing ring surface 13 against the valve support 12 via a return spring 17 and has a hollow cylindrical wall 16 which extends over a plurality of ribs 18 in the valve support 12.
  • a relief valve 19 operating as a check valve is essentially formed by a movable valve closing member 19a designed as a ball and an annular valve closing surface 20 of the valve closing body 15.
  • the valve closing body 15 has an expanding channel 21, which opens into the pressure line symbolized by an arrow 22, which leads to an injection valve, not shown.
  • a piston 36 which is only partially shown in the cylinder liner 11, delimits a working space 23 for the fuel to be injected.
  • the movable valve closing member 19 is pressed by a spring 28 via a first spring plate 33 against the valve closing surface 20 of the valve closing body 15 and is supported by a second spring plate 27 on a bracket which is formed by a bolt 24 in the example shown.
  • the bolt 24 has a substantially circular cross-sectional basic cross section, has a flat recess 25 in its central section 26, which forms the spring plate 27 receives a spring 28 of the check valve, and each of the two end sections, designated 29, of the bolt 24 each has a flat 30, both of which are arranged plane-parallel to the recess 25.
  • Two diametrically opposed openings 31 in the hollow cylindrical wall 16 serve as abutments for the bolt 24 and are formed by a bore drilled through the valve closing body 15 at right angles to a longitudinal axis 32.
  • the two end sections 29 of the bolt 24 are supported, which is additionally provided with two lateral flats 34, which run parallel to its longitudinal axis and also parallel to the longitudinal axis 32 of the valve closing body 15, in order to enlarge the return flow cross section (see FIG. 2). Because of this flow-enhancing shape, the bolt 24 can also be more easily gripped and assembled, and it can also be manufactured as an inexpensive molded part. Since the diameter of the basic cross section of the bolt 24 is selected to be the same as the diameter of the bores 31, a sufficiently large contact surface 35 in the form of a section of a cylindrical jacket surface remains for the mounting of the bolt 24 in the bores 31.

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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

Das Widerlager eines Entlastungsventiles (19) in einem Gleichdruckentlastungsventil (9) der Kraftstoff-Einspritzpumpe besteht aus einem Bolzen (24) und zwei diesen aufnehmenden Öffnungen (31) in der hülsenförmigen Wand (16) des beweglichen Ventilschließkörpers (15). Die Öffnungen (31) werden von einer rechtwinklig zür Längsachse (32) des Ventilschließkörpers (15) durch die Wand (16) desselben hindurchgebohrten Bohrung gebildet. Der Bolzen (24) nimmt in einer Vertiefung (25) einen Federteller (27) einer Feder (28) des Entlastungsventiles (19) auf und ist dadurch lagegesichert.The abutment of a relief valve (19) in a constant pressure relief valve (9) of the fuel injection pump consists of a bolt (24) and two openings (31) receiving these in the sleeve-shaped wall (16) of the movable valve closing body (15). The openings (31) are formed by a bore drilled at right angles to the longitudinal axis (32) of the valve closing body (15) through the wall (16) of the same. The bolt (24) receives a spring plate (27) of a spring (28) of the relief valve (19) in a recess (25) and is thereby secured in position.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoff-Einspritzpumpe für Brennkraftmaschinen nach der Gattung des Hauptanspruchs. Bei bekannten mit einem Gleichdruckentlastungsventil ausgestatteten Einspritzpumpen (CH-PS 394 710) erfolgt die Abstützung der Feder des Entlastungsventils über ein Schraubteil, das im hülsenförmigen Abschnitt des Ventilschließkörpers befestigt ist. Nachteilig an dieser Schraubverbindung ist es, daß wegen eines möglichen Lösens die sichere Funktion der Einspritzpumpe nicht immer gegeben ist, denn in den Pumpenarbeitsraum fallende Teile des Ventils können zu schwerwiegenden Schäden an der Einspritzpumpe und Folgeschäden an der Brennkraftmaschine führen.The invention relates to a fuel injection pump for internal combustion engines according to the preamble of the main claim. In known injection pumps equipped with a constant pressure relief valve (CH-PS 394 710), the spring of the relief valve is supported by a screw part which is fastened in the sleeve-shaped section of the valve closing body. The disadvantage of this screw connection is that because of a possible loosening, the safe functioning of the injection pump is not always given, because parts of the valve falling into the pump work space can lead to serious damage to the injection pump and consequential damage to the internal combustion engine.

Vorteile der ErfindungAdvantages of the invention

Mit der Kraftstoff-Einspritzpumpe für Brennkraftmaschinen nach der Erfindung wird der zum Stand der Technik dargelegte Nachteil mit einfachen Mitteln und auch unter ungünstigen Betriebsbedingungen mit Sicherheit vermieden. Der Erfindung liegt der Gedanke zugrunde, die hohlzylindrische Wand des Ventilschließkörpers als Widerlager zu nutzen.With the fuel injection pump for internal combustion engines according to the invention, the disadvantage set out in the prior art is avoided with simple means and with certainty even under unfavorable operating conditions. The invention is based on the idea of using the hollow cylindrical wall of the valve closing body as an abutment.

Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen beschrieben. Mit der Ausgestaltung der Kraftstoff-Einspritzpumpe nach Anspruch 2 wird ein in der Fertigung einfach herstellbares Widerlager geschaffen. Bei Einspritzpumpen, deren Feder des Entlastungsventils sich über einen Federteller im Ventilschließkörper abstützt, wird eine günstige Abstützung des Federtellers und zugleich eine Lagesicherung des Bügels durch die Merk- . male des Anspruchs 3 erreicht. Mit der Ausgestaltung des Bügels nach Anspruch 4 oder nach Anspruch 5 ist ein verbesserter Kraftstoffdurchfluß und eine sichere Funktion, sichere Montage und billige Herstellung des Bügels, z. B. als Preßteil, gewährleistet.Advantageous developments of the invention are described in the subclaims. With the configuration of the fuel injection pump according to claim 2, an abutment that is easy to manufacture is created. In injection pumps, the spring of the relief valve is supported by a spring plate in the valve closing body, a favorable support of the spring plate and at the same time a securing of the bracket by the Merk-. male of claim 3 achieved. With the design of the bracket according to claim 4 or claim 5 is an improved fuel flow and a safe function, safe assembly and cheap manufacture of the bracket, for. B. as a pressed part.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der Beschreibung näher erläutert. Figur 1 zeigt abschnittsweise eine Kraftstoff-Einspritzpumpe mit dem erfindungsgemäßen Gleichdruckentlastungsventil in vergrößertem Axialschnitt und Figur 2 zeigt eine Teilansicht des Ventilschließkörpers in Richtung des Pfeiles II in Figur 1 gesehen.An embodiment of the invention is shown in the drawing and explained in more detail in the description. 1 shows in sections a fuel injection pump with the constant pressure relief valve according to the invention in an enlarged axial section and FIG. 2 shows a partial view of the valve closing body in the direction of arrow II in FIG. 1.

Beschreibung des AusführungsbeispielesDescription of the embodiment

Von einer Kraftstoff-Einspritzpumpe zeigt Figur 1 ein als Gleichdruckentlastungsventil wirkendes Druckventil 9, dessen Ventilträger 12 mit einer Ventilsitzringfläche 13 zwischen einer Zylinderbuchse 11 und einem Druckstück 14 in einem Pumpengehäuse 10 befestigt ist. Ein beweglicher Ventilschließkörper 15 wird über eine Rückstellfeder 17 mit seiner Ventilschließringfläche 13 an den Ventilträger 12 gedrückt und hat eine hohlzylinderförmige Wand 16, die sich über mehrere Rippen 18 im Ventilträger 12 führt.From a fuel injection pump, FIG. 1 shows a pressure valve 9 acting as a constant pressure relief valve, the valve carrier 12 of which is fastened in a pump housing 10 with a valve seat ring surface 13 between a cylinder liner 11 and a pressure piece 14. A movable valve closing body 15 is pressed with its valve closing ring surface 13 against the valve support 12 via a return spring 17 and has a hollow cylindrical wall 16 which extends over a plurality of ribs 18 in the valve support 12.

Ein als Rückschlagventil arbeitendes Entlastungsventil 19 ist im wesentlichen von einem als Kugel ausgebildeten, beweglichen Ventilschließglied 19a und einer kreisringförmigen Ventilschließfläche 20 des Ventilschließkörpers 15 gebildet. Der Ventilschließkörper 15 weist einen sich erweiternden Kanal 21 auf, der in die durch einen Pfeil 22 symbolisierte Druckleitung mündet, die zu einem nicht gezeichneten Einspritzventil führt. Ein in der Zylinderbuchse 11 geführter, nur teilweise dargestellter Kolben 36 begrenzt einen Arbeitsraum 23 für den einzuspritzenden Kraftstoff. Das bewegliche Ventilschließglied 19 wird von einer Feder 28 über einen ersten Federteller 33 an die Ventilschließfläche 20 des Ventilschließkörpers 15 gedrückt und stützt sich mittels eines zweiten Federtellers 27 an einem Bügel ab, der im dargestellten Beispiel von einem Bolzen 24 gebildet ist.A relief valve 19 operating as a check valve is essentially formed by a movable valve closing member 19a designed as a ball and an annular valve closing surface 20 of the valve closing body 15. The valve closing body 15 has an expanding channel 21, which opens into the pressure line symbolized by an arrow 22, which leads to an injection valve, not shown. A piston 36, which is only partially shown in the cylinder liner 11, delimits a working space 23 for the fuel to be injected. The movable valve closing member 19 is pressed by a spring 28 via a first spring plate 33 against the valve closing surface 20 of the valve closing body 15 and is supported by a second spring plate 27 on a bracket which is formed by a bolt 24 in the example shown.

Der Bolzen 24 hat einen im wesentlichen kreisflächenförmigen Grundquerschnitt, weist in seinem Mittelabschnitt 26 eine ebene Vertiefung 25 auf, die den Federteller 27 einer Feder 28 des Rückschlagventils aufnimmt, und jeder der beiden mit 29 bezeichneten Endabschnitte des Bolzens 24 hat je eine Abflachung 30, die beide planparallel zur'Vertiefung 25 angeordnet sind. Als Widerlager für den Bolzen 24 dienen zwei einander diametral gegenüberliegende, in der hohlzylinderischen Wand 16 angebrachte Öffnungen 31, die von einer rechtwinklig zu einer Längsachse 32 durch den Ventilschließkörper 15 hindurchgebohrten Bohrung gebildet sind.The bolt 24 has a substantially circular cross-sectional basic cross section, has a flat recess 25 in its central section 26, which forms the spring plate 27 receives a spring 28 of the check valve, and each of the two end sections, designated 29, of the bolt 24 each has a flat 30, both of which are arranged plane-parallel to the recess 25. Two diametrically opposed openings 31 in the hollow cylindrical wall 16 serve as abutments for the bolt 24 and are formed by a bore drilled through the valve closing body 15 at right angles to a longitudinal axis 32.

In den Öffnungen 31 stützen sich die beiden Endabschnitte 29 des Bolzens 24 ab, der zur Vergrößerung des Rückflußquerschnittes zusätzlich noch mit zwei seitlichen, parallel zu seiner Längsachse und auch parallel zur Längsachse 32 des Ventilschließkörpers 15 verlaufenden Abflachungen 34 versehen ist (siehe Figur 2). Aufgrund dieser den Durchfluß verbessernden Formgebung kann der Bolzen 24 auch leichter angepackt und montiert werden, und er kann außerdem als billiges Formpreßteil hergestellt werden. Da der Durchmesser des Grundquerschnittes des Bolzens 24 gleich dem Durchmesser der Bohrungen 31 gewählt ist, verbleibt für die Lagerung des Bolzens 24 in den Bohrungen 31 eine genügend große Auflagefläche 35 in Form eines Abschnittes einer Zylindermantelfläche.In the openings 31, the two end sections 29 of the bolt 24 are supported, which is additionally provided with two lateral flats 34, which run parallel to its longitudinal axis and also parallel to the longitudinal axis 32 of the valve closing body 15, in order to enlarge the return flow cross section (see FIG. 2). Because of this flow-enhancing shape, the bolt 24 can also be more easily gripped and assembled, and it can also be manufactured as an inexpensive molded part. Since the diameter of the basic cross section of the bolt 24 is selected to be the same as the diameter of the bores 31, a sufficiently large contact surface 35 in the form of a section of a cylindrical jacket surface remains for the mounting of the bolt 24 in the bores 31.

Claims (5)

1. Kraftstoff-Einspritzpumpe für Brennkraftmaschinen mit einem einen Arbeitsraum (23) begrenzenden Kolben (36) und mit einem in die Druckleitung (22) zum Einspritzventil angeordneten Gleichdruckentlastungsventil (9), das gegen die Kraft einer Rückstellfeder (17) in Förderrichtung des Kraftstoffes öffnet und dessen beweglicher Ventilschließkörper (15) in einem Ventilträger (12) geführt ist und mit einem als Rückschlagventil ausgebildeten Entlastungsventil (19) versehen ist, dessen bewegliches Ventilschließglied (19a) sich über eine am Ventilschließkörper (15) abstützende Feder (28) entgegen Förderrichtung des Kraftstoffes öffnet und von der Feder (28) gegen eine am Ventilschließkörper (15) angeordnete Ventilsitzfläche (20) gedrückt wird, dadurch gekennzeichnet, daß ein Bügel (24) in zwei rechtwinklig zur Längsachse (32) des Ventilschließkörpers (15) angeordnete Öffnungen (31) der Wand (16) des Druckventils (9) eingesetzt ist und daß die mit dem beweglichen Ventilschließglied ( 19a) des Entlastungsventils (19) zusammenwirkende Feder (28) sich am Mittelabschnitt (26) des Bügels (24) abstützt.1. Fuel injection pump for internal combustion engines with a piston (36) delimiting a working space (23) and with a pressure relief valve (9) arranged in the pressure line (22) to the injection valve, which opens against the force of a return spring (17) in the direction of delivery of the fuel and the movable valve closing body (15) is guided in a valve carrier (12) and is provided with a relief valve (19) designed as a check valve, the movable valve closing member (19a) of which is supported against the direction of conveyance by a spring (28) supporting the valve closing body (15) Fuel opens and is pressed by the spring (28) against a valve seat surface (20) arranged on the valve closing body (15), characterized in that a bracket (24) is arranged in two openings (31) arranged at right angles to the longitudinal axis (32) of the valve closing body (15) ) the wall (16) of the pressure valve (9) is inserted and that with the movable valve closing member (19a) of the Relief valve (19) cooperating spring (28) is supported on the central portion (26) of the bracket (24). 2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die den Bügel (24) aufnehmenden Öffnungen (31) von einer rechtwinklig zur Längsachse (32) des Ventilschließkörpers (15) durch dessen zylindrische Wand (16) hindurchgebohrten Bohrung (31) gebildet sind.2. Pump according to claim 1, characterized in that the bracket (24) receiving openings (31) of a perpendicular to the longitudinal axis (32) of the valve closing body (15) through its cylindrical wall (16) through hole (31) are formed. 3. Pumpe nach Anspruch 1 oder 2 mit einem Federteller (33) für die Feder (28) des Entlastungsventils (19), dadurch gekennzeichnet, daß im Mittelabschnitt (26) des Bügels (24) eine den Federteller (27) aufnehmende Vertiefung (25) ausgespart ist.3. Pump according to claim 1 or 2 with a spring plate (33) for the spring (28) of the relief valve (19), characterized in that in the central portion (26) of the bracket (24) has a recess (25) receiving the spring plate (27) ) is left out. 4. Pumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Bügel als Bolzen (24) ausgebildet ist und einen kreisflächenförmigen Grundquerschnitt aufweist, dessen Durchmesser dem Durchmesser der Bohrung (31) entspricht, und daß die beiden Endabschnitte (29) des Bolzens (24) mindestens je eine planparallel zur Vertiefung (25) angeordnete Abflachung (30) aufweisen.4. Pump according to claim 2 or 3, characterized in that the bracket is designed as a bolt (24) and has a circular cross-section, the diameter of which corresponds to the diameter of the bore (31), and that the two end portions (29) of the bolt ( 24) each have at least one flattened portion (30) arranged parallel to the depression (25). 5. Pumpe nach Anspruch 4, dadurch gekennzeichnet, daß der Bolzen (24) außer den an seinen Endabschnitten (29) befindlichen Abflachungen (30) zusätzlich noch zwei parallel zu seiner Längsachse und zur Längsachse (32) des Ventilschließkörpers (15) angeordnete Abflachungen (34) aufweist und sich mit einer als Abschnitt einer Zylindermantelfläche ausgebildeten Auflagefläche (35) in den Öffnungen (31) abstützt (Figur 2).5. Pump according to claim 4, characterized in that the bolt (24) in addition to the flats (30) located at its end portions (29) in addition two parallel to its longitudinal axis and to the longitudinal axis (32) of the valve closing body (15) arranged flats ( 34) and is supported in the openings (31) with a support surface (35) designed as a section of a cylindrical surface (FIG. 2).
EP19820107462 1981-09-04 1982-08-17 Fuel injection pump for internal-combustion engines Withdrawn EP0073967A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3134971 1981-09-04
DE3134971 1981-09-04
DE19823221405 DE3221405A1 (en) 1981-09-04 1982-06-05 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3221405 1982-06-05

Publications (1)

Publication Number Publication Date
EP0073967A1 true EP0073967A1 (en) 1983-03-16

Family

ID=25795765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820107462 Withdrawn EP0073967A1 (en) 1981-09-04 1982-08-17 Fuel injection pump for internal-combustion engines

Country Status (3)

Country Link
US (1) US4459086A (en)
EP (1) EP0073967A1 (en)
DE (1) DE3221405A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4664084A (en) * 1985-07-29 1987-05-12 Teledyne Industries, Inc. Fuel metering system
US4714412A (en) * 1983-07-27 1987-12-22 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
CN110107253A (en) * 2018-01-30 2019-08-09 中国石油化工股份有限公司 Back-pressure valve for high temperature and pressure rock core flowing experiment

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
DE3341575C2 (en) * 1983-11-17 1996-06-05 Bosch Gmbh Robert Pressure valve for fuel injection pumps
GB2172665B (en) * 1985-02-06 1988-07-27 Aisin Seiki Hydraulic pump assemblies
IT206877Z2 (en) * 1985-10-22 1987-10-12 Weber Spa CONSTANT PRESSURE DELIVERY VALVE FOR FUEL INJECTION PUMPS FOR DIESEL CYCLE ENGINES
JPS63151972U (en) * 1987-03-27 1988-10-05
DE3874720T2 (en) * 1988-01-16 1993-07-01 Lucas Ind Plc PRESSURE CONTROL VALVE.
DE19706591A1 (en) * 1997-02-20 1998-08-27 Bosch Gmbh Robert Pressure valve
DE19941688C2 (en) * 1999-09-01 2001-08-09 Siemens Ag Injection device for an internal combustion engine with direct injection
DE10346813B4 (en) * 2003-10-06 2013-08-29 I F M Electronic Gmbh An optoelectronic sensor and method for detecting an object in a surveillance area
IT1394070B1 (en) * 2009-05-13 2012-05-25 Bosch Gmbh Robert VALVE ASSEMBLY FOR CHECKING THE SUPPLY AND FUEL FLOW OF A COMPRESSION CHAMBER OF A HIGH PRESSURE PISTON PUMP AND HIGH PRESSURE PISTON PUMP INCLUDING SUCH VALVE GROUP
US9181944B2 (en) * 2011-03-31 2015-11-10 Denso Corporation High pressure pump having unitary discharge and relief valve
JP5920636B2 (en) * 2013-09-13 2016-05-18 株式会社デンソー High pressure pump

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US1999967A (en) * 1933-03-29 1935-04-30 Ingersoll Rand Co Valve mechanism
US2247421A (en) * 1938-06-18 1941-07-01 Eisemann Magneto Corp Pressure regulator for fuel injection systems for internal combustion engines
CH394710A (en) * 1962-08-09 1965-06-30 Schweizerische Lokomotiv Fuel injection pump for internal combustion engines
US3309024A (en) * 1965-01-07 1967-03-14 Int Harvester Co Fuel delivery valve and injection apparatus employing same
DE1297935B (en) * 1965-06-03 1969-06-19 Kloeckner Humboldt Deutz Ag Fuel injection system

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Publication number Priority date Publication date Assignee Title
DE1202545B (en) * 1962-07-21 1965-10-07 Ludwig Rexroth Pressure regulator

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1999967A (en) * 1933-03-29 1935-04-30 Ingersoll Rand Co Valve mechanism
US2247421A (en) * 1938-06-18 1941-07-01 Eisemann Magneto Corp Pressure regulator for fuel injection systems for internal combustion engines
CH394710A (en) * 1962-08-09 1965-06-30 Schweizerische Lokomotiv Fuel injection pump for internal combustion engines
US3309024A (en) * 1965-01-07 1967-03-14 Int Harvester Co Fuel delivery valve and injection apparatus employing same
DE1297935B (en) * 1965-06-03 1969-06-19 Kloeckner Humboldt Deutz Ag Fuel injection system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4714412A (en) * 1983-07-27 1987-12-22 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4664084A (en) * 1985-07-29 1987-05-12 Teledyne Industries, Inc. Fuel metering system
CN110107253A (en) * 2018-01-30 2019-08-09 中国石油化工股份有限公司 Back-pressure valve for high temperature and pressure rock core flowing experiment

Also Published As

Publication number Publication date
US4459086A (en) 1984-07-10
DE3221405A1 (en) 1983-03-24

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