EP3088725B1 - Kraftstoffpumpe für ein direkteinspritzsystem mit reduzierter belastung an der laufbuchse des kolbens - Google Patents

Kraftstoffpumpe für ein direkteinspritzsystem mit reduzierter belastung an der laufbuchse des kolbens Download PDF

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Publication number
EP3088725B1
EP3088725B1 EP16167581.4A EP16167581A EP3088725B1 EP 3088725 B1 EP3088725 B1 EP 3088725B1 EP 16167581 A EP16167581 A EP 16167581A EP 3088725 B1 EP3088725 B1 EP 3088725B1
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EP
European Patent Office
Prior art keywords
guide bushing
pumping chamber
annular abutment
fuel pump
piston
Prior art date
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Application number
EP16167581.4A
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English (en)
French (fr)
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EP3088725A1 (de
Inventor
Michele Petrone
Enrico Vezzani
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Marelli Europe SpA
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Magneti Marelli SpA
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Publication of EP3088725A1 publication Critical patent/EP3088725A1/de
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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
    • F02M59/44—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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9007—Ceramic materials
    • 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
    • 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
    • F02M59/445—Selection of particular materials

Definitions

  • the present invention relates to a fuel pump for a direct injection system; preferably, the direct injection system is used in an internal combustion engine with controlled ignition, and then supplied with petrol or similar fuels.
  • a direct injection system comprises a plurality of injectors, a common rail that supplies the pressurized fuel to the injectors, a high-pressure fuel pump, which supplies the fuel to the common rail by means of a high-pressure supply duct and is provided with a flow-regulating device, and a control unit which controls the flow-regulating device to maintain the fuel pressure inside the common rail at a desired value, generally variable over time as a function of the engine operating conditions.
  • the high-pressure fuel pump described in the patent application EP2236809A1 comprises a pumping chamber within which a piston slides with reciprocating motion, an intake channel controlled by an intake valve for supplying the low-pressure fuel within the pumping chamber, and a delivery channel regulated by a delivery valve for feeding the high-pressure fuel out of the pumping chamber and into the common rail through the supply duct.
  • the pressure of the intake valve is normally controlled and, in the absence of any external intervention, the intake valve is closed when the fuel pressure in the pumping chamber is higher than the fuel pressure in the intake channel, and is open when the fuel pressure in the pumping chamber is lower than the fuel pressure in the intake channel.
  • the flow-regulating device is mechanically coupled to the intake valve to maintain, when necessary, the intake valve open during the pumping phase of the piston, thus allowing a fuel flow to come out of the pumping chamber through the intake channel.
  • the flow-regulating device comprises a control rod, which is coupled to the intake valve and is movable between a passive position, where the rod allows the closing of the intake valve, and an active position, where the rod does not allow the closing of the intake valve.
  • the flow-regulating device also comprises an electromagnetic actuator, which is coupled to the control rod to move the control rod between the active position and the passive position.
  • the electromagnetic actuator comprises a spring, which keeps the control rod in the active position, and an electromagnet that moves the control rod into the passive position, magnetically attracting a ferromagnetic anchor integral with the control rod against a fixed magnetic armature.
  • the reciprocating sliding of the piston is guided by a guide bushing, which is arranged below the pumping chamber to delimit inferiorly the pumping chamber and inside which the piston slides.
  • the guide bushing is fitted in a containing seat, which is formed below the pumping chamber.
  • the piston guide bushing is subjected to high mechanical stresses, since it must withstand the hydraulic thrust generated during pumping, which acts on the circular crown-shaped surface defined between the inner diameter and the outer diameter of the guide bushing; in this regard, there is a significant difference between the inner diameter and the outer diameter of the guide bushing (approximately, the inner diameter is about 7-9 mm, while the outer diameter is about 14-16 mm), and therefore the hydraulic thrust on the guide bushing is significant.
  • the object of the present invention is to provide a fuel pump for a direct injection system, said fuel pump being able to pump fuel at high pressures and being at the same time easy and economical to produce.
  • the present invention accordingly provides a fuel pump for a direct injection system according to what claimed by the appended claims.
  • the number 1 indicates in its entirety a fuel direct injection system of the common rail type for an internal combustion engine.
  • the direct injection system 1 comprises a plurality of injectors 2, a common rail 3 that supplies the pressurized fuel to the injectors 2, a high-pressure pump 4, which feeds the fuel to the common rail 3 by means of a supply duct 5 and is provided with a flow-regulating device 6, a control unit 7 that maintains the fuel pressure inside the common rail 3 at a desired value, generally variable over time as a function of the engine operating conditions, and a low-pressure pump 8 which feeds the fuel from a tank 9 to the high-pressure pump 4 through a supply duct 10.
  • the control unit 7 is coupled to the flow-regulating device 6 to control the flow of the high-pressure pump 4, to supply, instant by instant, to the common rail 3 the amount of fuel required to obtain the desired pressure value in the common rail 3.
  • the control unit 7 regulates the flow rate of the high-pressure pump 4 by means of a feedback control using as a feedback variable the value of the fuel pressure in the common rail 3, the pressure value being detected in real time by a pressure sensor 11.
  • the high-pressure pump 4 comprises a main body 12, which has a longitudinal axis 13 and defines inside it a cylindrical pumping chamber 14.
  • a piston 15 is slidably mounted inside the pumping chamber 14. Moving with a reciprocating motion along the longitudinal axis 13, the piston 15 causes a cyclic variation of the volume of the pumping chamber 14.
  • a lower portion of the piston 15 is coupled on one side to a spring 16, which tends to push the piston 15 toward a position of maximum volume of the pumping chamber 14, and on the other side to a cam (not shown) that is brought in rotation by an engine crankshaft to cyclically move upwards the piston 15, thus compressing the spring 16.
  • a side wall of the pumping chamber 14 originates an intake channel 17 that is connected to the low-pressure pump 8 via the supply duct 10 and is regulated by an intake valve 18 arranged at the pumping chamber 14.
  • the pressure of the intake valve 18 is normally controlled and, in the absence of any external intervention, the intake valve 18 is closed when the fuel pressure in the pumping chamber 14 is higher than the fuel pressure in the intake channel 17, and is open when the fuel pressure in the pumping chamber 14 is lower than the fuel pressure in the intake channel 17.
  • a delivery channel 19 originates on a side wall of the pumping chamber 14 and on the opposite side with respect to the intake channel 17, said channel being connected to the common rail 3 by means of the supply duct 5 and being regulated by a unidirectional delivery valve 20 which is arranged at the pumping chamber 14 and allows only a flow of fuel out of the pumping chamber 14.
  • the pressure of the delivery valve 20 is controlled and the valve is opened when the fuel pressure in the pumping chamber 14 is higher than the fuel pressure in the delivery channel 19, and is closed when the fuel pressure in the pumping chamber 14 is lower than the fuel pressure in the delivery channel 19.
  • the flow-regulating device 6 is mechanically coupled to the intake valve 18 to allow the control unit 7, when necessary, keeping the intake valve 18 open during a pumping phase of the piston 15 and then to allow a fuel flow going out of the pumping chamber 14 through the intake channel 17.
  • the flow-regulating device 6 comprises a control rod 21, which is coupled to the intake valve 18 and is movable between a passive position, where it allows the closing of the intake valve 18, and an active position, where it does not allows the closing of the intake valve 18.
  • the flow-regulating device 6 also comprises an electromagnetic actuator 22, which is coupled to the control rod 21 to move the control rod 21 between the active position and the passive position.
  • a side wall of the pumping chamber 14 originates an exhaust channel 23, which connects the pumping chamber 14 with the delivery channel 19 and is regulated by a unidirectional maximum pressure valve 24 allowing only a flow of fuel entering the pumping chamber 14.
  • the function of the maximum pressure valve 24 is to allow a fuel outlet in the case where the fuel pressure in the common rail 3 exceeds a maximum value set at the design stage (typically in case of control errors made by the control unit 7); in other words, the maximum pressure valve 24 is calibrated to automatically open when the pressure jump at its ends is higher than a threshold value set in the design phase, and thus prevent the fuel pressure in the common rail 3 from exceeding the maximum value set in the design phase.
  • a cylindrical containing seat 26 housing a guide bushing 27 of the piston 15 is formed in the main body 12 and below the pumping chamber 14.
  • the guide bushing 27 inferiorly delimits the pumping chamber 14 (i.e. forms a bottom wall of the pumping chamber 14), and drives the reciprocating axial sliding.
  • the guide bushing 27 is made of a material having a suitable hardness and a surface finish to facilitate the axial sliding of the piston 15.
  • the guide bushing 27 is fastened in the containing seat 26 by fitting the guide bushing 27 in the containing seat 26 or by a side caulking of the guide bushing 27 in the containing seat 26.
  • the containing seat 26 has a diameter (significantly) larger than the pumping chamber 14 so that the guide bushing 27 inserted in the containing seat 26 can inferiorly delimit the pumping chamber 14.
  • the containing seat 26 is delimited on top by an annular abutment 28, which externally has the diameter of the containing seat 26 and internally has the diameter of the pumping chamber 14.
  • the guide bushing 27 has a tubular shape and is internally provided with a through hole 29 slidingly housing the piston 15; the through hole 29 of the guide bushing 27 substantially has the same diameter of the piston 15 housing the piston 15 with no appreciable clearance, and therefore has a diameter smaller than the one of the pumping chamber 14.
  • the guide bushing 27 On top (namely towards the pumping chamber 14), the guide bushing 27 has an annular surface 30 which abuts against the annular abutment 28 of the containing seat 26 and forms the lower delimitation of the pumping chamber 14.
  • the upper surface 30 of the guide bushing 27 has a convex shape having an increasing height from outside to inside; in other words, the upper surface 30 of the guide bushing 27 is not perfectly parallel to the annular abutment 28 of the containing seat 26, but has an increasing height from outside to inside. Therefore, the upper surface 30 of the guide bushing 27 is rounded to be externally lower and internally higher. Moreover, the annular abutment 28 of the containing seat 26 has a centrally arranged step 31, against which a central portion of the upper surface 30 of the guide bushing 27 rests.
  • the convex shape of the upper surface 30 of the guide bushing 27 and the step 31 of the annular abutment 28 of the containing seat 26 determine that the contact between the upper surface 30 of the guide bushing 27 and the annular abutment 28 of the containing seat 26 occurs always and only at the step 31 (i.e. at the edge of the step 31) for a clear geometric constraint.
  • the guide bushing 27 is fitted in the containing seat 26 and is pushed against the annular abutment 28 with a force sufficient to cause a plastic deformation in the contact area of the annular abutment 28 or the upper surface 30 of the guide bushing 27.
  • the guide bushing 27 is made of a metallic material harder than the metal material forming the annular abutment 28 (or forming the main body 12 having a housing seat 26) so that a plastic deformation of the annular abutment 28 (at the step 31) against the upper surface 30 of the guide bushing 27 occurs in the contact area.
  • the guide bushing 27 is made of a metallic material less hard than the metal material forming the annular abutment 28 (or forming the main body 12 having a housing seat 26) so that a plastic deformation of the guide bushing 27 (at the step 31) against the annular abutment 28 occurs in the contact area.
  • the plastic deformation occurring at the step 31 allows to obtain a perfect contact (i.e. with no cracks, however small) between the upper surface 30 of the guide bushing 27 28 and the annular abutment of the containing seat 26. This guarantees an optimal hydraulic sealing, showing no leakage even at very high fuel pressures (even higher than 1000 bars).
  • the guide bushing 27 and/or the piston 15 can be made of a ceramic material, which can have a considerable hardness and favourable frictional characteristics.
  • the guide bushing 27 and the piston 15 are made of a ceramic material, the guide bushing 27 is easily harder than the annular abutment 28 so that a plastic deformation of the shoulder 28 against the upper annular surface 30 of the guide bushing 27 occurs in the contact area.
  • the guide bushing 27 and the piston 15 are made of a ceramic material, a very low friction between the bushing 27 and the driving piston 15 can be obtained.
  • the high-pressure pump 4 as described above has numerous advantages.
  • the aforesaid high-pressure pump 4 can pump fuel at a pressure above 600-700 bars.
  • this result is obtained thanks to the fact that the hydraulic thrust on the guide bushing 27 of the piston 15 is significantly limited by moving to the inside the contact point (i.e., the hydraulic sealing area) between the upper surface 30 of the guide bushing 27 and the annular abutment 28 of the containing seat 26.
  • the aforesaid high-pressure pump 4 is economic and easy to implement, because the changes, compared to a similar known fuel pump, are limited to two simple mechanical machining steps; substantially, the upper surface 30 of the guide bushing 27 must be machined to give a convex shape to the upper surface 30 and the shoulder 28 of the containing seat 26 must be machined to create the step 31 (both of these machining steps are simple and, above all, are mainly carried out on the single parts before they are assembled).

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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 (6)

  1. Kraftstoffpumpe (4) für ein Direkteinspritzsystem, das mit einer gemeinsamen Kraftstoffleitung (3) versehen ist, welche Kraftstoffpumpe (4) aufweist:
    eine Pumpenkammer (14), die in einem Hauptkörper (12) gebildet ist;
    einen Kolben (15), der innerhalb der Pumpenkammer (14) verschiebbar angebracht ist, um das Volumen der Pumpenkammer (14) zyklisch zu variieren;
    einen Einlasskanal (17), der von einer Wand der Pumpenkammer (14) entspringt;
    ein Einlassventil (18), das entlang dem Einlasskanal (17) angeordnet ist;
    einen Abgabekanal (19), der von einer Wand der Pumpenkammer (14) entspringt;
    ein Abgabeventil (20), das entlang dem Abgabekanal (19) angeordnet ist;
    einen zylindrischen Aufnahmesitz (26), der in dem Hauptkörper (12) unter der Pumpenkammer (14) gebildet ist, einen Durchmesser hat, der größer ist als der Durchmesser der Pumpenkammer (14), und auf der Oberseite durch einen ringförmigen Anschlag (28) begrenzt ist, der an der Außenseite den Durchmesser des Aufnahmesitzes (26) hat und an der Innenseite den Durchmesser der Pumpenkammer (14); und
    eine Führungsbuchse (27), die in dem Aufnahmesitz (26) untergebracht ist, mittig mit einer Durchgangsbohrung (29) versehen ist, wo der Kolben (15) verschiebbar angeordnet ist, und eine obere Oberfläche (30) hat, die an dem ringförmigen Anschlag (28) des Aufnahmesitzes (26) anliegt;
    wobei die obere Oberfläche (30) der Führungsbuchse (21) und der ringförmige Anschlag (28) des Aufnahmesitzes (26) so geformt sind, dass sie zwischen sich eine hydraulische Dichtung schaffen, die in einem mittleren Bereich des ringförmigen Anschlags (28) gebildet ist; und
    wobei der ringförmige Anschlag (28) des Aufnahmesitzes (26) eine Abstufung (31) hat, die mittig angeordnet ist und an welcher ein Mittelteil der oberen Oberfläche (30) der Führungsbuchse (27) anliegt;
    wobei die Kraftstoffpumpe (4) dadurch gekennzeichnet ist, dass die obere Oberfläche (30) der Führungsbuchse (27) eine abgerundete und konvexe Form hat, die von außen nach innen eine ansteigende Höhe hat, sodass die obere Oberfläche (30) außen niedriger und innen höher ist.
  2. Kraftstoffpumpe (4) nach Anspruch 1, wobei die Führungsbuchse (27) in den Aufnahmesitz (26) eingesetzt ist und gegen den ringförmigen Anschlag (28) mit einer Kraft gedrückt wird, die ausreicht, um eine plastische Verformung im Kontaktgebiet des ringförmigen Anschlags (28) oder der oberen Oberfläche (30) der Führungsbuchse (27) hervorzurufen.
  3. Kraftstoffpumpe (4) nach Anspruch 2, wobei die Führungsbuchse (27) aus einem Werkstoff hergestellt ist, der härter ist als der den ringförmigen Anschlag bildende Werkstoff, sodass in dem Kontaktgebiet eine plastische Verformung des ringförmigen Anschlags (28) gegen die obere Oberfläche (30) der Führungsbuchse (27) auftritt.
  4. Kraftstoffpumpe (4) nach Anspruch 2, wobei die Führungsbuchse (27) aus einem Werkstoff hergestellt ist, der weniger hart ist als der den ringförmigen Anschlag (28) bildende Werkstoff, sodass in dem Kontaktgebiet eine plastische Verformung der oberen Oberfläche (27) der Führungsbuchse (28) gegen den ringförmigen Anschlag (30) auftritt.
  5. Kraftstoffpumpe (4) nach einem der Ansprüche 1 bis 4, wobei die Führungsbuchse (27) aus einem Keramikwerkstoff hergestellt ist.
  6. Kraftstoffpumpe (4) nach einem der Ansprüche 1 bis 5, wobei der Kolben (15) aus einem Keramikwerkstoff hergestellt ist.
EP16167581.4A 2015-04-28 2016-04-28 Kraftstoffpumpe für ein direkteinspritzsystem mit reduzierter belastung an der laufbuchse des kolbens Active EP3088725B1 (de)

Applications Claiming Priority (1)

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ITBO20150210 2015-04-28

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EP3088725B1 true EP3088725B1 (de) 2019-07-03

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Cited By (2)

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DE102020203529B3 (de) 2020-03-19 2021-07-08 Vitesco Technologies GmbH Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug
DE102020200575A1 (de) 2020-01-20 2021-07-22 Vitesco Technologies GmbH Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug

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DE102020200575A1 (de) 2020-01-20 2021-07-22 Vitesco Technologies GmbH Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug
DE102020200575B4 (de) 2020-01-20 2021-07-29 Vitesco Technologies GmbH Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug
DE102020203529B3 (de) 2020-03-19 2021-07-08 Vitesco Technologies GmbH Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug

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