WO2012123131A1 - Dispositif soupape, notamment soupape d'échappement d'une pompe à carburant haute pression d'un moteur à combustion interne - Google Patents

Dispositif soupape, notamment soupape d'échappement d'une pompe à carburant haute pression d'un moteur à combustion interne Download PDF

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Publication number
WO2012123131A1
WO2012123131A1 PCT/EP2012/050222 EP2012050222W WO2012123131A1 WO 2012123131 A1 WO2012123131 A1 WO 2012123131A1 EP 2012050222 W EP2012050222 W EP 2012050222W WO 2012123131 A1 WO2012123131 A1 WO 2012123131A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
valve device
valve
sealing seat
valve body
Prior art date
Application number
PCT/EP2012/050222
Other languages
German (de)
English (en)
Inventor
Nadja Eisenmenger
Rainer Wilms
Valentin Szermutzky
Dominik Brunner
Hans-Christoph Magel
Matthias Maess
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 WO2012123131A1 publication Critical patent/WO2012123131A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
    • F16K15/028—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open the valve member consisting only of a predominantly disc-shaped flat element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0413—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K25/00—Details relating to contact between valve members and seats
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • Valve device in particular outlet valve of a high-pressure fuel pump of an internal combustion engine
  • the invention relates to a valve device according to the preamble of claim 1.
  • High pressure pump arranged quantity control valves take over the flow control. Furthermore, such a high-pressure pump has an outlet valve, which is prestressed, for example, by a valve spring and seals the fuel distributor against a delivery chamber of the high-pressure pump.
  • the outlet valve can open, provided that the pressure in the delivery chamber is greater than the pressure in the delivery chamber
  • the exhaust valve has a so-called flat seat with a comparatively large sealing seat width.
  • the large seal seat width is required to minimize wear of the exhaust valve over its life.
  • valve plate Sealing portion of the valve body (“valve plate”) of the exhaust valve and the Housing-tight sealing seat (“counter plate”) existing contact area filled with fuel.
  • counter plate Housing-tight sealing seat
  • an initially small gap is formed, which is rapidly increased by inflow of fuel.
  • the hydraulic pressure prevailing in the gap temporarily drops sharply, causing the valve plate to "stick” to the sealing seat for a short time.
  • the piston of the high-pressure pump is quickly moved further and compresses the fuel in the pumping chamber correspondingly quickly, the sticking creates a pressure peak in the pumping chamber and subsequently an undesired shockwave. As a result, pulsations of the fuel are excited and the operating noise of the high-pressure pump is increased.
  • valves such as a ball-and-cone valve
  • the moving mass is generally larger.
  • Patent publications from this field are, for example, DE 10 2006 055 832 A1, DE 10 2006 002 638 A1, DE 102 49 688 A1, DE 102 20 717 A1, DE 102 13 626 A1, and DE 101 38 362 A1 ,
  • the invention has the advantage that an adhesive effect when lifting a plate-shaped movable valve body is reduced by a housing-side sealing seat of a hydraulic valve device and the mass of the valve body is reduced.
  • a maximum delivery pressure can be reduced and the load on the housing of a high pressure pump and a required drive torque can be reduced.
  • the degree of rotation of the high-pressure pump improves, pressure pulsations are reduced and an operating noise is lowered.
  • the valve device according to the invention has a flow channel in which the plate-shaped valve body arranged therein can control or block a fluid flow together with the sealing seat.
  • the invention is based on the consideration that an adhesive effect on lifting of the valve body from the sealing seat is dependent on a surface of a contact region formed between a sealing portion of the valve body and the sealing seat. According to the invention, the area of the contact area is reduced by, when the valve device is closed, immediately adjacent to the contact area between
  • Sealing section and sealing seat a wedge-shaped gap is present. As a result, it is not necessary to form the valve body as a ball or as a cone, whereby space and mass moved are saved. At the same time, a leakage of the fluid to be controlled by the valve device can be kept small.
  • the invention provides that the wedge angle in the gap is at most about 15 °, more preferably at most about 5 °, even more preferably at most about 2 °.
  • the wedge angle in the gap is at most about 15 °, more preferably at most about 5 °, even more preferably at most about 2 °.
  • valve device provides that the valve body and / or the sealing seat in the sealing area is conical.
  • Sealing area is formed by the interaction of the housing-side sealing seat and the sealing portion. Due to the regional cone-shaped
  • Geometry of the valve body and / or the sealing seat properties of a cone valve can be achieved without too much sticking effect occurs when lifting the valve body, and without it being necessary to form the valve body as a complete cone.
  • valve device provides that the valve body is spherical in the sealing area or has a spherical convex curvature.
  • the adhesive effect can also be significantly reduced without the valve body being completely designed as a ball.
  • the spherical area or the spherical curvature may, for example, be made by machining or by cold working.
  • the valve body has a substantially central concave recess.
  • the concave recess may have an approximately spherical cap-like geometry, whereby a first boundary surface of the wedge-shaped gap according to the invention is formed. A second boundary surface is formed by the sealing portion.
  • a further embodiment of the valve device comprises a sealing seat which is spherical in the sealing region. This can - with a flat trained
  • inventive wedge-shaped gap can be achieved in the sealing area.
  • the "ball shape" of the sealing seat in the direction of
  • the axis of movement of the valve body to be "cut in half", so that still a - infinitesimal small - contact surface between the sealing seat and the sealing portion and thus a wedge-shaped gap are formed.
  • the remaining ball shape of the sealing seat has radially outward or radially inward.
  • the wedge-shaped gap is present only on one side of the sealing area, preferably on the downstream side. This enables a further advantageous embodiment of the valve device.
  • the valve device can be designed to be particularly simple if the valve body is dimensioned, in particular designed as a sufficiently thin plate, that it deforms when the valve device is closed due to the pressure difference across the sealing region and thereby produces the wedge-shaped gap.
  • the valve body can partially assume a spherical cap-like shape, which generates the gap according to the invention on an edge or on a surface of the sealing seat which is inclined with respect to the axis of movement of the valve device.
  • the sealing seat may be formed so that it has an edge in the contact area, such that when the valve device is closed, a largely linear contact between the valve body and sealing seat is present.
  • Switching cycles expanded to a narrow ring surface In addition, small bumps and / or manufacturing tolerances can be compensated.
  • a further embodiment of the valve device provides that the sealing seat upstream and / or downstream of the contact region has a circumferential chamfer. As a result, when the valve device is open, a hydraulic flow resistance is lowered and the efficiency is thus improved.
  • the dynamics of the valve device is further improved when the valve body has recesses outside an environment of the sealing portion.
  • Valve device can be improved.
  • regions of the valve body that are subject to greater stress-in particular within an environment of the sealing section- can optionally be stiffened in order to prevent or reduce elastic deformations of the valve body. This can be the
  • Fatigue strength of the valve device can be increased. Suitable areas can be determined, for example, by means of a computer simulation.
  • Figure 1 is a schematic sectional view of a high-pressure fuel pump with a first embodiment of a sealing region of a
  • Figure 2 is a sectional view of a second embodiment of the sealing area of the exhaust valve of Figure 1;
  • Figure 3 is a sectional view of a third embodiment of the sealing area;
  • FIG. 4 shows a sectional view of a fourth embodiment of the sealing region
  • Figure 5 is a sectional view of a fifth embodiment of the sealing area
  • FIG. 6 shows a sectional view of a sixth embodiment of the sealing region
  • FIG. 7 shows a sectional view of a seventh embodiment of the sealing region
  • FIG. 8 shows a sectional view of an eighth embodiment of the sealing region
  • Figure 9 is a sectional view of a ninth embodiment of the sealing area
  • Figure 10 is a sectional view of a tenth embodiment of the sealing portion
  • Figure 1 1 is a sectional view of an eleventh embodiment of the sealing area
  • Figure 12 is a sectional view of a twelfth embodiment of the sealing portion
  • Figure 13 is a sectional view of a thirteenth embodiment of the
  • FIG. 14 shows the sealing region of FIG. 13 in the case of a worn-off sealing seat.
  • FIG. 1 shows a fuel pump 10 of a fuel system of FIG
  • the fuel pump 10 has a housing 20, in whose left portion in the drawing, an electromagnet 15 with a coil 22, an armature 24 and an armature spring 26 is arranged. Furthermore, the fuel pump 10 comprises an inlet 28 connected to a low-pressure line 7 with an inlet valve 30, and an outlet 32 connected to a high-pressure line 11 with a Exhaust valve, which is hereinafter referred to as valve means 34.
  • the inlet valve 30 comprises a spring 31 and a valve element 33.
  • the valve element 33 can be moved by means of a valve needle 35, which can be moved horizontally in the drawing and coupled to the armature 24.
  • a piston 18 is arranged vertically movable in the drawing.
  • the piston 18 can be moved by means of a roller 40 of a - in this case elliptical - cam 17 in a cylinder 37.
  • the cylinder 37 is formed in a portion of the housing 20.
  • the inlet valve 30 is hydraulically connected via an opening 38 with the delivery chamber 36.
  • the arranged within the Gepuruse0 20 volumes of the fuel pump 10 are substantially with
  • a substantially plate-shaped valve body 42 of the valve device 34 (outlet valve) has an approximately spherical cap-shaped sealing section 44, which cooperates with a sealing seat 46 formed by an end face of an axial and housing-fixed collar.
  • a wedge-shaped gap 50 is present between the sealing portion 44 and the sealing seat 46.
  • valve body 42 has a central recess 52.
  • the sealing seat 46 is formed on an annular end portion 53 of the housing 20 and aligned substantially perpendicular with respect to a longitudinal axis 48.
  • the sealing seat 46 and the sealing portion 44 lie on one another and form at the contact point a substantially linear contact area 54.
  • the fuel pump 10 delivers fuel from the inlet 28 to the outlet 32, the valve means 34 opening or closing corresponding to a respective pressure difference between the delivery space 36 and the outlet 32.
  • the valve body 42 of the valve device 34 in the direction of
  • valve device 34 the functional elements of the valve device 34 are designed to be rotationally symmetrical about the longitudinal axis 48. However, this is not explicitly stated again.
  • valve means 34 are shown in an open or partially opened state for better illustration.
  • the geometries shown, in particular the wedge-shaped gap 50, for the purpose of better illustration partially exaggerated.
  • FIG. 2 shows a second embodiment of the sealing region of the valve device 34, which is closed in the present case, in a sectional view.
  • the valve body 42 in the right region of the drawing is designed similarly to the figure 1 and thus has a partially spherical or spherical contour.
  • the sealing seat 46 has a circumferential chamfer 56 upstream and downstream of the contact region 54.
  • Contact area 54 are transformed due to elastic and plastic deformations to a narrow annular surface contact. Nevertheless, the effective (annular) area of the contact region 54 generally remains relatively small.
  • FIG. 3 shows a third embodiment of the sealing area. In the present case is the
  • the annular end portion 53 of the housing 20, which is shown in the left-hand area of the drawing, has conical contours in some regions radially inward and radially outward.
  • the sealing seat 46 is arranged on the annular end portion 53 in such a way that the sealing seat 46 is tilted (radially encircling) with respect to the longitudinal axis 48, ie is slightly conical.
  • the wedge-shaped gap 50 and, correspondingly, the line-shaped contact region 54 are formed between the sealing seat 46 and the sealing section 44.
  • FIG. 4 shows a fourth embodiment of the sealing region.
  • the sealing seat 46 and the sealing portion 44 with respect to the longitudinal axis 48 per se at right angles and flat.
  • the radially inner portions of the elastic and comparatively thin valve body 42 are slightly inclined to the left and right in the drawing the radially outer sections are bent to the right.
  • An auxiliary line 60 drawn at right angles to the longitudinal axis 48 additionally illustrates this.
  • Fatigue resistance may be required that the valve body 42 has a particularly elastic material with a high yield strength.
  • FIG. 5 shows a fifth embodiment of the sealing area.
  • the sealing seat 46 is tilted radially in relation to a plane perpendicular to the longitudinal axis 48 by an angle W1.
  • the wedge-shaped gap 50 radially inward
  • the linear contact region 54 radially outward
  • FIG. 5 an edge 61 is designated in the contact region 54.
  • the sealing seat 46 has two chamfers 62 each having an angle W2 and W3, which form the line-shaped contact region 54 at a vertex. Accordingly, between the sealing seat 46 and the sealing portion 44 two wedge-shaped
  • Column 50 each formed radially inward and radially outward.
  • the angles W2 and W3 can also have mutually different values.
  • a ratio d2 / d1 of the distances d1 and d2 may be in a range of zero to one.
  • FIG. 7 shows a seventh embodiment of the sealing region.
  • the sealing seat 46 has a spherical contour symmetrical to a line 64 parallel to the longitudinal axis 48.
  • a - at least theoretically - linear contact region 54 and two wedge-shaped gaps 50 are likewise formed.
  • Figures 8 and 9 show an eighth and a ninth embodiment of the sealing area. Starting from the embodiment of FIG. 7, the radially inner and outer portions of the line 64 are crowned
  • FIG. 10 shows a tenth embodiment of the sealing region.
  • the valve body 42 has a central concave recess 66.
  • the sealing seat 46 is aligned at right angles to the longitudinal axis 48.
  • FIG. 11 shows an eleventh embodiment of the sealing area.
  • the valve body 42 has a circumferential and radially outwardly directed
  • FIG. 12 shows a twelfth embodiment of the sealing region.
  • the valve body 42 has a circumferential and radially inwardly directed
  • Form contact area 54 and a wedge-shaped gap 50 Form contact area 54 and a wedge-shaped gap 50.
  • Figure 13 shows a thirteenth embodiment of the sealing region, wherein the valve device 34 is shown in the closed state.
  • the annular end section 53 of the housing 20 has a radially circumferential recess 72. Accordingly, a radial dimension 74 of the end portion 53 is reduced by a radial dimension 76, so that the surface of the sealing seat 46 is comparatively small.
  • the sealing seat 46 and the sealing portion 44 with respect to the longitudinal axis 48 are rectangular and planar.
  • the valve body 42 - similar to Figure 4 - as a result of the prevailing at the outlet 32 high fuel pressure according to the arrow 58 is bent radially. As a result, an annular contact region 54 and a wedge-shaped gap 50 are again formed.
  • FIG. 14 shows the sealing region of FIG. 13 after a longer service life of the valve device.
  • Contact area 54 now includes the entire between the sealing seat 46 and the sealing portion 44 possible contact surface.
  • Sealing seat 46 but the force to be overcome is comparatively low.
  • the end portion 53 is designed such that even with a further wear on the sealing seat 46 said contact surface is not further increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne un dispositif soupape (34), notamment une soupape d'échappement d'une pompe à carburant haute pression (10) d'un moteur à combustion interne, comportant un carter (20), un canal d'écoulement et un corps soupape (42) mobile en forme de plaque disposé dans le canal d'écoulement, présentant un segment d'étanchéité (44) s'appuyant par endroits contre un siège d'étanchéité (46) côté carter lorsque le dispositif soupape (34) est fermé. Les segments mutuellement en contact du segment d'étanchéité (44) et du siège d'étanchéité (46) forment une zone de contact (54) et lorsque le dispositif soupape (34) est fermé, une fente cunéiforme (50) est présente au moins temporairement de façon directement adjacente à la zone de contact (54) entre le segment d'étanchéité (44) et le siège d'étanchéité (46).
PCT/EP2012/050222 2011-03-14 2012-01-09 Dispositif soupape, notamment soupape d'échappement d'une pompe à carburant haute pression d'un moteur à combustion interne WO2012123131A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110005487 DE102011005487A1 (de) 2011-03-14 2011-03-14 Ventileinrichtung, insbesondere Auslassventil einer Kraftstoff-Hochdruckpumpe einer Brennkraftmaschine
DE102011005487.1 2011-03-14

Publications (1)

Publication Number Publication Date
WO2012123131A1 true WO2012123131A1 (fr) 2012-09-20

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Country Status (2)

Country Link
DE (1) DE102011005487A1 (fr)
WO (1) WO2012123131A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN109210246A (zh) * 2017-07-03 2019-01-15 大陆汽车系统公司 组合式入口和出口止回阀座

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
DE102012221540A1 (de) * 2012-11-26 2014-05-28 Robert Bosch Gmbh Ventileinrichtung
DE102015201520A1 (de) * 2015-01-29 2016-08-04 Robert Bosch Gmbh Verstelleinrichtung und Brennstoffeinspritzanlage mit einer Verstelleinrichtung
DE102018206763A1 (de) * 2018-05-02 2019-11-07 Robert Bosch Gmbh Ventileinrichtung für eine Hochdruckpumpe
DE102019210653A1 (de) * 2019-07-18 2021-01-21 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem einer Brennkraftmaschine
DE102019210655A1 (de) * 2019-07-18 2021-01-21 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem und Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
DE102019210654B4 (de) * 2019-07-18 2023-12-14 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem einer Brennkraftmaschine

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US3664371A (en) * 1970-10-23 1972-05-23 Us Navy Resilient poppet valve
US3830255A (en) * 1972-11-24 1974-08-20 Fmc Corp Valve assembly
DE2449443A1 (de) * 1974-10-17 1976-04-29 Heilmeier & Weinlein Rueckschlagventil
DE10059954A1 (de) * 2000-12-02 2002-06-13 Jopp Gmbh Rückschlagventil
DE10138362A1 (de) 2001-04-06 2002-10-17 Bosch Gmbh Robert Einstempel-Einspritzpumpe für ein Common-Rail-Kraftstoffeinspritzsystem
DE10213626A1 (de) 2002-03-27 2003-10-23 Bosch Gmbh Robert Hochdruck-Kraftstoffpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
DE10220717A1 (de) 2002-05-10 2003-11-27 Bosch Gmbh Robert Magnetventil, insbesondere Mengensteuerventil für Kraftstoffsysteme von Brennkraftmaschinen
EP1411238A1 (fr) * 2002-10-15 2004-04-21 Robert Bosch Gmbh Soupape de limitation de pression pour un system d'injection de carburant
DE10327411A1 (de) * 2002-10-15 2004-04-29 Robert Bosch Gmbh Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
DE10249688A1 (de) 2002-10-25 2004-05-06 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Kraftstoffeinspritzanlage, insbesondere eine Common-Rail-Kraftstoffeinspritzanlage, von Brennkraftmaschinen
DE102006002638A1 (de) 2006-01-19 2007-07-26 Robert Bosch Gmbh Magnetventil
DE102007016134A1 (de) * 2006-04-25 2007-11-08 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102006051570A1 (de) * 2006-11-02 2008-05-08 Schaeffler Kg Rückschlagventil mit variabler Einstellung des Öffnungsdrucks
DE102006055832A1 (de) 2006-11-27 2008-05-29 Robert Bosch Gmbh Integrierbares Rückschlagventil
WO2009063306A1 (fr) * 2007-11-16 2009-05-22 Toyota Jidosha Kabushiki Kaisha Appareil d'alimentation en carburant haute pression pour moteur à combustion interne
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Publication number Priority date Publication date Assignee Title
US2710023A (en) * 1951-08-22 1955-06-07 Durabla Mfg Company Check-unit or valve
US3664371A (en) * 1970-10-23 1972-05-23 Us Navy Resilient poppet valve
US3830255A (en) * 1972-11-24 1974-08-20 Fmc Corp Valve assembly
DE2449443A1 (de) * 1974-10-17 1976-04-29 Heilmeier & Weinlein Rueckschlagventil
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DE10138362A1 (de) 2001-04-06 2002-10-17 Bosch Gmbh Robert Einstempel-Einspritzpumpe für ein Common-Rail-Kraftstoffeinspritzsystem
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DE10220717A1 (de) 2002-05-10 2003-11-27 Bosch Gmbh Robert Magnetventil, insbesondere Mengensteuerventil für Kraftstoffsysteme von Brennkraftmaschinen
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DE10327411A1 (de) * 2002-10-15 2004-04-29 Robert Bosch Gmbh Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
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DE102006051570A1 (de) * 2006-11-02 2008-05-08 Schaeffler Kg Rückschlagventil mit variabler Einstellung des Öffnungsdrucks
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WO2009063306A1 (fr) * 2007-11-16 2009-05-22 Toyota Jidosha Kabushiki Kaisha Appareil d'alimentation en carburant haute pression pour moteur à combustion interne
DE102008043217A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine

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CN109210246A (zh) * 2017-07-03 2019-01-15 大陆汽车系统公司 组合式入口和出口止回阀座
US10883458B2 (en) 2017-07-03 2021-01-05 Vitesco Technologies USA, LLC. Asymmetric spring valve disk
US11105437B2 (en) 2017-07-03 2021-08-31 Continental Automotive Systems, Inc. Combined inlet and outlet check valve seat
US11231032B2 (en) 2017-07-03 2022-01-25 Vitesco Technologies USA, LLC Fuel sending unit assembly and operation

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