EP3091220B1 - Hochdruckbrennstoffpumpe - Google Patents

Hochdruckbrennstoffpumpe Download PDF

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Publication number
EP3091220B1
EP3091220B1 EP16168225.7A EP16168225A EP3091220B1 EP 3091220 B1 EP3091220 B1 EP 3091220B1 EP 16168225 A EP16168225 A EP 16168225A EP 3091220 B1 EP3091220 B1 EP 3091220B1
Authority
EP
European Patent Office
Prior art keywords
plunger
cam ring
spacer element
foot portion
cam surface
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.)
Active
Application number
EP16168225.7A
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English (en)
French (fr)
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EP3091220A1 (de
Inventor
James T. D. MCHATTIE
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.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
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Filing date
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Application filed by Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3091220A1 publication Critical patent/EP3091220A1/de
Application granted granted Critical
Publication of EP3091220B1 publication Critical patent/EP3091220B1/de
Active 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • 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
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs

Definitions

  • the present invention generally relates to the field of internal combustion engines and more specifically to a high pressure fuel pump, in particular to a high pressure fuel pump for a common rail fuel injection system in a diesel engine.
  • the high pressure fuel pump is the interface between the low pressure and high pressure stages of fuel delivery of an internal combustion engine. Its function is to make sure that there is always sufficient fuel under high pressure in all engine operation conditions. At the same time, the high pressure pump must operate for the entire service life of a vehicle. Furthermore, a fuel reserve has to be provided for example for a quick start or rapid pressure rise in the common rail. As a result, the high-pressure pump supplies constantly high pressure fuel to the common rail independent of the requirement of the injection process.
  • a pump housing accommodates a set of 3 pumping units driven by a drive shaft rotatably supported in the pump housing.
  • the pumping units are radially arranged with respect to the drive shaft, and circumferentially spaced by 120°. They include each a plunger reciprocally movable in a bore to form a pressure chamber.
  • the drive shaft comprises an eccentric segment located inside the housing and an outer ring member is provided to the drive shaft eccentric segment. This ring member has, at its outer periphery, three flat surfaces at an offset of 120° with each other; and each pump plunger rests on such a flat surface of the ring member.
  • a return spring is provided to prestress the pump plunger bottom against the flat surface of the ring member.
  • the drive shaft's eccentric section is rotated with respect to the ring member, causing displacement of the flat surfaces in radial direction.
  • the flat surfaces of the ring member move in cyclic order, alternately towards and away from the axis of rotation of the drive shaft, forcing the pump plungers to axially move reciprocally in the bore.
  • US 4 108 130 A discloses another high pressure fuel pump with a C-shaped spring.
  • the above design of high pressure fuel pumps using pumping units driven by a central drive shaft with eccentric is widely used.
  • the durability expectations place the existing plunger return spring design at the very limit of the material property.
  • the plunger return spring to maintain contact between the plunger end and the shaft eccentric segment, extends and compresses many millions of times to perform its function. The failure of the spring is thus of concern.
  • the object of the present invention is to provide a high pressure pump having an improved design. This object is achieved by a high pressure fuel pump as claimed in claim 1.
  • a high pressure fuel pump for an internal combustion engine comprises a pumping unit comprising a (fixed) body with a bore therein and a plunger reciprocally (axially) movable in the bore, the plunger having a front portion defining, with said bore, a pressure chamber in said bore and an opposite foot portion; and drive means for driving the plunger by its foot portion.
  • the drive means comprise a cam ring arranged to be rotatable about an axis, the cam ring having an inner peripheral surface defining an inner cam surface.
  • the pumping unit is positioned so as to be surrounded by the cam ring with the plunger foot portion being arranged to follow the inner cam surface of the cam ring in such a way that the rotation of the cam ring causes the plunger to reciprocate in its respective bore.
  • the present high pressure fuel pump proposes a design wherein pumping unit is surrounded by the cam ring and in fact completely contained in the pump assembly. Accordingly, in case of failure of the pumping body, fuel will not leak outward but inside the cam ring, which is itself surrounded by the pump housing.
  • the abutment means preferably comprise a spacer element extending in the reciprocating direction of the plunger having a length selected in such a way that, in any position of the cam ring, a first end of said spacer is in contact with said foot portion of said plunger, while the opposite second end of said spacer rests against said inner cam surface.
  • the spacer element is axially moveable in the reciprocating direction of said plunger, so that it may keep a fixed length during pump operation.
  • the spacer element takes the form of a U-shaped element having two legs united by a transverse bottom section, the outer ends of the legs forming the first end of the spacer element, whereas the second end of the spacer element is formed by the bottom section.
  • the legs of the spacer element may then be placed on both sides of the pumping body (e.g. having an elongate shape in the reciprocating direction of the plunger) to asssit in the axial guiding of the spacer element.
  • the spacer element may be made from a resilient material, preferably metallic, in particular steel, to provide a pre-loading force.
  • the plunger foot portion rests against the inner cam surface via a skid element, the foot potion being pressed against said skid by the first end of the spacer element; and the second end of the spacer element rests against the inner cam surface via another skid element.
  • the skid elements which assist in the conversion between rotational and axial movements, may be configured as rectangular pads having a curved side in contact with the cam surface and an opposite flat side against which the plunger foot portion or spacer element rests.
  • the inner cam surface may be a circular surface having a center axis offset with regard to the rotation axis of the cam ring.
  • the inner cam surface may thus be referred to as eccentric cam surface.
  • those skilled in the art may devise other cam surface shapes, for example to increase the number of strokes per cam ring revolution.
  • the pump may comprise a housing with a back plate on which the body is fixedly arranged and a cover having an inner cylindrical cavity accommodating the revolving cam ring.
  • the cam ring is rotationally driven by a revolving drive shaft, which may be made in one piece (integral) with the cam ring or rotationally coupled thereto.
  • Figure 1 shows a cross section of an embodiment of the present high pressure fuel pump 10 for supplying fuel to a fuel injection system in an internal combustion engine.
  • the pump is used, for example, in a common rail injection system for supplying fuel to the internal combustion engine.
  • Such a pump typically receives the fuel from the vehicle tank at about 2 to 5 bars and delivers a high pressure of up to 2000 bars and even higher to the common rail of the fuel injection system.
  • the common rail in turn supplies the fuel to the fuel injectors.
  • the pump 10 comprises a housing generally indicated 12, which includes a front cover 14 fixed to a plate 16 also referred to as 'back plate'. Inside the housing 12, a pumping unit 18 also referred to as 'pumping head' is fixedly positioned to the back plate 16.
  • This pumping unit 18 comprises a body 20 having a blind bore 22 therein.
  • the body 20 may have an elongate block shape, e.g. parallelepipedic, and may be manufactured in one part with the back plate or is fixed thereto in any appropriate way.
  • the bore 22 extends from one of the two end faces 24a and 24b of the body 20.
  • a piston or plunger 26 is reciprocally movable in the bore 22 of the body and has a matching diameter inside the bore.
  • a front portion 28 of the plunger defines with the bore a pressure chamber 30.
  • the plunger 26 of the pumping unit 18 further comprises a foot portion 32, which may include an end plate 34.
  • the bore 22 has an inlet for supplying fuel to the pressure chamber 30 and an outlet for delivering pressurized fuel.
  • the inlet provides fuel from the tank to the pressure chamber 30 and the outlet allows delivering fuel under high pressure to the common rail and towards the injectors of the internal combustion engine.
  • the inlet and outlet may be each controlled by a respective valve unit allowing or obturating the flow of fuel therethrough.
  • Pump 10 further comprises drive means for driving plunger 26 by its foot portion 32.
  • the drive means comprise a cam ring 40 having an inner peripheral surface 42 outlining an inner cam surface.
  • the cam ring 40 is driven in rotation by a drive shaft 43 that is rotatably mounted in the housing 12.
  • the pumping unit 18 is positioned so as to be surrounded by the cam ring 40.
  • the foot portion 32 of the plunger is configured to follow the cam surface 42 of the cam ring to cause the reciprocal motion of the latter.
  • the cam ring 42 may herein generally take the form of a solid ring having an outer peripheral surface 44 and an inner peripheral surface 42 that are radially separated by the body of the ring.
  • the inner peripheral surface 42 herein forms the desired surface for driving the plunger 26 and is thus designated “inner cam surface”.
  • the cam ring 40 is preferably closed on one side by a cover plate 44, on the other side of which the drive shaft 43 is connected.
  • the cam ring 40 can be manufactured in any appropriate way.
  • One can e.g. start from a circular solid cylinder or disk and machine therein a circular bore to obtain a ring element.
  • the ring element is manufactured from such disk but the circular bore is machined as blind bore, so that the cam ring 40 includes the cover 44.
  • the drive shaft 43 may be manufactured in one piece with such cam ring and cover, or simply assembled to the cam ring and cover element.
  • the outer peripheral surface 44 of cam ring 40 is a circular surface having a central axis A that defines the revolving axis of cam ring 40.
  • the cam surface 42 is a circular surface, the center A' of which is offset with respect to the ring axis A.
  • the inner cam surface 42 is thus also referred to as eccentric cam.
  • the pumping unit 18 is surrounded by the cam ring 40.
  • the pumping unit extends across the cam ring with the end faces 24a, 24b of the pumping body 20 facing the inner cam surface 42, and fits inside the cavity defined by the cam ring (appropriate depth is thus required). In use, this cavity is filled with fuel.
  • the a fuel inlet (receiving low pressure fuel from the tank) and a fuel outlet are provided in the back plate, with respective valve means, to control the flow of fuel through the cavity.
  • the foot portion 32 of the plunger is arranged to follow the inner cam surface 42 of the cam ring 40 in such a way that the rotation of the cam ring causes the plunger 26 to move axially in bore 22, thereby reciprocally driving the plunger.
  • a spacer element 48 that can also be generally referred to as abutment means, in order to maintain the contact between the foot portion 32 and the driving inner cam surface 42.
  • the spacer element 48 extends in the reciprocating direction of the plunger and has a length selected in such a way that, in any position of the cam ring, a first end of the spacer is in contact with the plunger foot portion, while the opposite second end of the spacer rests against the inner cam surface. But contrary to a conventional spring, the spacer element's length remains substantially constant during operation and is not designed to undergo deformation.
  • the spring clip 48 has two legs 50 united by a transverse bottom section 52.
  • the free ends 54 of the legs form the first end of the spacer, whereas the second end of said spacer is formed by said bottom section 52.
  • the spring clip is preferably made of a material with some resilience, typically a metallic material, e.g. steel.
  • the spring clip is not designed to undergo deformation in use (contrary to the conventional return spring as in EP 2 093 421 ), it however supports a slight load to prestress the plunger foot portion 32 against its respective skid 56.
  • Figs. 4 to 7 schematically illustrate the pump 10 in four operational configurations.
  • the spring clip 48 is used to acts as spacer or stud so that the plunger foot 32 can follow the cam surface 42.
  • the eccentric cam surface 42 rotates, the distance between the cam surface 42 and top body surface 24a changes.
  • Spring clip 48 ensures contact between the foot portion 32 and cam surface 42, causing the plunger 26 to reciprocate in bore 22.
  • spring clip 48 is movable in the reciprocating direction of plunger 26 and actually is preferably designed to have its branches 48 slide along the outer flat sides of body block 20, aligning the clip 48 in its sliding direction.
  • the spring clip 48 rests at both ends onto the cam surface 42 via respective skid elements 56.
  • the skids 56 are configured as interface elements that aid to convert the circular motion of the eccentric cam surface 42 into a linear motion.
  • the skid element 56 here takes the form of a rectangular pad having a curved side 58 in contact with the cam surface and an opposite flat side 60 against which the plunger foot portion 34, , respectively the clip bottom, rests. Hence, the plunger 26 and spring clip 48 technically rest indirectly against cam surface 42 via the respective skid elements 56.
  • the curved surface 58 of the skid 56 has a curvature radius preferably matching that of the cam surface 42.
  • the dimensions of the flat side 60 are chosen to maintain contact with the foot portion 34 as the skid moves transversely with respect to the spring clip 48, as will be explained below. Since the inner cavity of the cam ring 40 is filled with fuel, a film of fuel exists between the skid's curved surface 48 and the inner cam surface 42, facilitating the sliding.
  • the plunger 26 is at the top-most position (TDC) in the chamber 30.
  • the thicker part of the eccentric cam 40 is located below the pumping body, the bottom face 24b thereof being very close to the skid; whereas the thinner part of the cam ring 40 is above the plunger foot portion 32.
  • This position corresponds to the end of the filling stroke, the pressure chamber 30 has its largest volume and is filled with fuel.
  • cam ring 40 As the cam ring rotates (counter clockwise with respect to the Figs.), the thicker part of cam ring 40 moves to the side and the cam ring portion above the foot portion 32 becomes thicker. This causes the plunger 26 to move into the bore 22 of pumping body 20: this is the pumping stroke.
  • the foot portion 32 and spring clip base 52 are centered on their respective skids 56.
  • the rotation axis of the cam ring A and center A' of the eccentric cam surface 42 are vertically aligned (with reference to the figure).
  • the center A' of the circular cam surface 42 rotates around the fixed center A of the cam ring 40. Due to the eccentricity, and since the skids 56 are maintained at diametrically opposite position by the fixed length clip 48, the skids 56 need to move to follow the curvature of the inner cam surface 42. Since the pumping body 20 is fixed and the clip 48 can only move in the plunger's reciprocating direction, the width of the skid flat surface 60 needs to be designed to allow relative displacement of the plunger flat end 34, respectively clip base 52.
  • the rotation axis A of the cam ring (center of outer peripheral surface 44) preferably crosses the central axis B of the bore 22 (defining the plunger's reciprocating axis).
  • the rotation axis A and the cam center A' are aligned on the central axis B.
  • the distance A-A' is the maximum stroke of the pumping unit. In practice, the offset distance A-A' may be selected in the range of 2 to 6 mm.
  • the length L S ( Fig.6 ) of the flat side 60 of the skid 56 should be at least equal to the length of the flat side L F plus twice the offset distance A-A'.
  • the height of the spring clip 48 corresponds to the diameter of the inner cam 42 minus the thickness t ( Fig.6 ) of the two skids 56. Since the skids are able to move relative to the spring clip 48, the spring clip 48 keeps its length.
  • the cover 14 comprises a cylindrical section 14 1 surrounding the cam ring 40 and a front plate 14 2 axially blocking the cam ring 40.
  • the inner diameter of cylindrical section 14 1 is adapted to serve as bearing to rotatably accommodated cam ring 40.
  • Front plate 141 has a central opening 14 3 for the drive shaft 43. If desirable, this central opening 14 3 may further be shaped as a bearing section to assist in the rotation of the drive shaft 43 and particularly take up load applied on the external portion of the drive shaft 43, e.g. by a driving belt.
  • Another way to explore may be to vary the shape of the inner cam surface, e.g. in order to perform more than one couple of in and out strokes per cam ring revolution.
  • a couple of pumping units could be arranged in the cavity of the cam ring 40.
  • the two plungers could be made axially integral in movement, whereby only one abutment means/spring clip may be used.
  • the two pumping units could also be arranged in an axially inverted fashion (one plunger upwards, the other downwards). In such case, the abutment means may simply consist in a blocking link that makes the two plungers axially locked.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (7)

  1. Hochdruckkraftstoffpumpe für einen Verbrennungsmotor, die aufweist:
    eine Pumpeinheit (18), die einen Körper (20) mit einer darin befindlichen Bohrung (22) und einem in der Bohrung hin- und herbewegbaren Kolben (26) aufweist, wobei der Kolben einen vorderen Abschnitt hat, der mit der Bohrung eine Druckkammer (30) in der Bohrung definiert, und einen gegenüberliegenden Fußabschnitt (32);
    Treibermittel zum Treiben des Kolbens durch seinen Fußabschnitt;
    wobei die Treibermittel einen Nockenring (40) aufweisen, der ausgebildet ist, um eine Achse (A) rotierbar zu sein, wobei der Nockenring eine innere Nockenoberfläche (42) hat;
    wobei die Pumpeinheit (18) derart positioniert ist, dass sie von dem Nockenring (40) umgeben ist, wobei der Kolbenfußabschnitt (32) angeordnet ist, der inneren Nockenoberfläche (42) des Nockenrings (40) zu folgen derart, dass die Rotation des Nockenrings bewirkt, dass sich der Kolben in der Bohrung (22) hin- und herbewegt; aufweisend Anschlagmittel, die konfiguriert sind, um den Fußabschnitt (32) des Kolbens (26) in Treiberkontakt mit der inneren Nockenoberfläche (42) zu halten,
    wobei die Anschlagmittel ein Abstandselement (48) aufweisen, das sich in der Hin- und Herbewegungsrichtung des Kolbens erstreckt, mit einer Länge, die derart ausgewählt ist, dass in jeder Position des Nockenrings ein erstes Ende des Abstandshalters in Kontakt mit dem Fußabschnitt des Kolbens ist,
    wobei der Kolbenfußabschnitt (32) an der inneren Nockenoberfläche über ein Schlittenelement (56) anliegt, wobei der Fußabschnitt durch das erste Ende des Abstandselements gegen den Schlitten gedrückt wird; und das zweite Ende des Abstandselements (48) an der inneren Nockenoberfläche über ein anderes Schlittenelement (56) anliegt, dadurch gekennzeichnet, dass
    der Körper (20) der Pumpeinheit eine längliche Form in der Hin- und Herbewegungsrichtung des Kolbens (26) hat;
    das Abstandselement (48) ein U-förmiges Element ist mit zwei durch einen querverlaufenden unteren Abschnitt (52) verbundenen Schenkeln (50), wobei die äußeren Enden der Schenkel das erste Ende des Abstandselements bilden, während das zweite Ende des Abstandselements durch den unteren Abschnitt gebildet ist;
    die Schenkel (50) des Abstandselements auf beiden Seiten des Körpers zu dessen axialer Führung angeordnet sind.
  2. Die Pumpe gemäß Anspruch 1, wobei die innere Nockenoberfläche (42) eine kreisförmige Fläche mit einer Mittelachse (A') ist, die in Bezug auf die Rotationsachse (A) des Nockenrings (40) versetzt ist.
  3. Die Pumpe gemäß Anspruch 1, wobei das Abstandselement (48) in der Hin- und Herbewegungsrichtung des Kolbens axial bewegbar ist.
  4. Die Pumpe gemäß Anspruch 1, wobei die Schlitten als rechteckige Kissen mit einer gekrümmten Seite in Kontakt mit der Nockenoberfläche und einer gegenüberliegenden flachen Seite konfiguriert sind.
  5. Die Pumpe gemäß einem der Ansprüche 1 bis 4, wobei das Abstandselement aus einem elastischen Material, vorzugsweise Metall, insbesondere Stahl, hergestellt ist, um eine Vorspannkraft vorzusehen.
  6. Die Pumpe gemäß einem der vorhergehenden Ansprüche, die ein Gehäuse aufweist mit einer Rückplatte, auf der der Körper fest angeordnet ist, und einer Abdeckung mit einem inneren zylindrischen Hohlraum, der den umlaufenden Nockenring aufnimmt.
  7. Die Pumpe gemäß einem der vorhergehenden Ansprüche, wobei der Nockenring (40) durch eine umlaufende Antriebswelle (43) rotierend angetrieben wird, wobei die Antriebswelle integral mit dem Nockenring ist oder mit diesem rotierbar gekoppelt ist.
EP16168225.7A 2015-05-06 2016-05-04 Hochdruckbrennstoffpumpe Active EP3091220B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1507704.3A GB201507704D0 (en) 2015-05-06 2015-05-06 High-pressure fuel pump

Publications (2)

Publication Number Publication Date
EP3091220A1 EP3091220A1 (de) 2016-11-09
EP3091220B1 true EP3091220B1 (de) 2018-10-17

Family

ID=53489175

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16168225.7A Active EP3091220B1 (de) 2015-05-06 2016-05-04 Hochdruckbrennstoffpumpe

Country Status (2)

Country Link
EP (1) EP3091220B1 (de)
GB (1) GB201507704D0 (de)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4108130A (en) * 1977-05-18 1978-08-22 Caterpillar Tractor Co. Fuel injection pump
JP2001515566A (ja) * 1998-01-15 2001-09-18 スタナダイン オートモーティヴ コーポレイション エンジンに装着された駆動軸受を有する液圧ポンプ
CN100526634C (zh) * 2008-04-30 2009-08-12 福建省莆田市中涵机动力有限公司 柴油机高压共轨燃油系统供油泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
GB201507704D0 (en) 2015-06-17
EP3091220A1 (de) 2016-11-09

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