WO2019120822A1 - Soupape, en particulier soupape d'aspiration, dans une pompe à haute pression d'un système d'injection de carburant - Google Patents

Soupape, en particulier soupape d'aspiration, dans une pompe à haute pression d'un système d'injection de carburant Download PDF

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Publication number
WO2019120822A1
WO2019120822A1 PCT/EP2018/081829 EP2018081829W WO2019120822A1 WO 2019120822 A1 WO2019120822 A1 WO 2019120822A1 EP 2018081829 W EP2018081829 W EP 2018081829W WO 2019120822 A1 WO2019120822 A1 WO 2019120822A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
armature
guide sleeve
valve body
sliding layer
Prior art date
Application number
PCT/EP2018/081829
Other languages
German (de)
English (en)
Inventor
Steffen Holm
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 WO2019120822A1 publication Critical patent/WO2019120822A1/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
    • F02M59/20—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
    • F02M59/368—Pump inlet valves being closed when actuated
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
    • 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
    • F02M2200/9053—Metals
    • F02M2200/9061—Special treatments for modifying the properties of metals used for fuel injection apparatus, e.g. modifying mechanical or electromagnetic properties

Definitions

  • Valve in particular a mammoth valve, in a high-pressure pump of a fuel injection system
  • a valve in particular an electrically actuated valve, a high-pressure pump of a fuel injection system is known from DE 10 2014 214 811 Al.
  • the electrically actuated valve has a valve element which is movable between an open and a closed position, with a magnet armature which is in mechanical contact with the valve element in the axial direction and which abuts against a first compression spring on the side facing away from the valve element, and wherein the armature is axially movable by an electromagnetic control and is in a starting position on a stop plate on a valve body supported.
  • the armature is part of an electro-magnetic actuator, which also includes a magnetic coil.
  • an electrically operated valve with the features of claim 1 has the advantage that tilting and / or one-sided partial abutment of a magnet armature is prevented in a valve body, as a sliding layer for improved guidance of the armature in the valve body provides and almost no clearance due to Toleranzabweichun conditions radially to a longitudinal axis between the gas tanker and the Ventilkör results.
  • a tilting and / or a one-sided partial concerns of the armature can be almost completely prevented due to the improved radial tolerances of the guide. This results on the one hand he increased life of the electrically operated valve and thus an entire high-pressure pump, and on the other hand, a lower probability of failure of the electrically operated valve.
  • the embodiment of the electrically actuated valve according to claim 1 has the advantage that an avoidance and / or reduction of material removal and damage to the valve body is achieved. Furthermore, the advantage can be achieved that undesired fluctuating valve switching times and / or delayed switching times due to the tilted magnet armature are prevented.
  • the subclaims relate to preferred developments of the invention.
  • the magnet armature is at least approximately completely covered by the sliding layer on an outer circumference facing away from the longitudinal axis, wherein the sliding layer is non-positively and / or materially connected to the magnet armature.
  • the valve body on one of the longitudinal axis facing inner surface may be at least partially covered by the sliding layer, wherein the sliding layer is non-positively and / or materially verbun with the valve body is the. Due to this inventive design of the electric actuator should accounted valve can be achieved that the components armature and valve body are not directly in contact and / or in Appendix. The components are thus in contact with each other only indirectly via the sliding layer.
  • the sliding layer is designed as a guide sleeve, wherein the guide sleeve is made of a friction-reducing and / or low-friction material.
  • the guide sleeve may have self-lubricating properties, in particular by the use of carbon and / or graphite.
  • the life of the sliding layer can be increased, since the imple mentation as a guide sleeve is also structurally so stable that a Ablö sen of the sliding layer of the armature and / or the valve body can be prevented and also prevent that can be a disadvantageous deformation adjusts the sliding layer, which would reduce the guiding properties and prevent reliable axial movement of the armature in the valve body.
  • Another advantage of the inventive feature of the electrically operated valve is that due to the self-lubricating properties of the Füh approximately sleeve axial lifting movement of the armature in the valve body, in particular special in the leadership of the valve body, can be done with a lower resistance due to friction between the friction partners. As a result, on the one hand, the actuation energy for controlling the valve can be reduced, which in turn leads to savings in operating costs. Furthermore, the self-lubricating properties of the guide sleeve reduces the friction energy which occurs, whereby the temperatures in the region of the magnet armature and of the valve body can be reduced. This leads to an increased Le life of the components solenoid armature, valve body and the surrounding construction parts, such as a pole core.
  • the magnet armature is surrounded by a lubricating medium, in particular oil. Due to the reduced frictional heat aging of the lubricating medium is reduced due to increased heat exposure in this exemplary embodiment, which increases the life of the Schmiermedi ums and the probability of failure of the electrically operated valve is reduced.
  • each of the magnetic anchor and the valve body on the sliding layer or the guide sleeve has a higher strength and / or hardness ge compared to the material of the magnet armature and / or the valve body.
  • the friction between the components armature and valve body can be further reduced in a highly dynamic switching movements of the magnet armature, since the two components are not directly related to each other in Kon- stand, since only the sliding layer and / or the guide sleeve are in frictional contact with each other.
  • the at least one guide sleeve is displaced in a rotation extending about the longitudinal axis, to then be slid coaxially either on the outer circumference of the armature and / or pushed onto the inner surface in the valve body.
  • the connection between the guide sleeve and the armature or the valve body may be designed as a positive connection.
  • the guide sleeve is thermally treated prior to assembly, that increases the inner diameter of the guide sleeve reversibly and temporarily limited, which is reduced after the successful installation of the guide sleeve on the armature of the réelle manmes ser the guide sleeve and thus a frictional connection with forms the outer periphery of the armature, in particular by means of egg ner surface pressure.
  • the guide sleeve additionally experiences an increase in the strength and / or hardness of the material of the guide sleeve due to the thermal treatment in the same method step.
  • the guide sleeve in the valve body and / or on the armature can be converted, resulting in a reduction of assembly time and installation costs.
  • the armature and / or the valve body is not affected, for example, by a thermal energy input, as is the case with welding, whereby possible occurring effects on the armature and / or the valve body are reduced by the assembly process.
  • the thermal treat ment of the guide sleeve which is carried out in the same process step and by means of which an increase in the strength and / or hardness of the guide sleeve is achieved, carried out prior to introduction into the valve body or the application to the armature, in particular a reduction or a Increasing the inner diameter or the outer diameter of the Füh approximately sleeve before assembly to effect.
  • the advantage can be achieved that the life of the guide sleeve can be improved by means of a single assembly step and at the same time a quick and inexpensive installation can be done. In this way, the cost of the electric valve can be reduced and at the same time the life of the electric valve and thus the entire high-pressure pump can be increased.
  • FIG. 2 shows a designated in Figure 1 with II section of the pump in verierter representation with an electrically operated valve
  • FIG. 3 shows a section of the electrically operated valve, designated by III in FIG. 2, in an enlarged view according to a first exemplary embodiment
  • Figure 4 shows a designated in Figure 2 with III section of the electrically be actuated valve in an enlarged view according to a second embodiment.
  • Fig. 1 shows a sectional view of a high-pressure pump 1 shown schematically, which is designed as a high-pressure fuel pump 1 and is preferably installed in a common rail injection system.
  • the high-pressure pump 1 is provided by a fuel low-pressure system having at least one tank, a filter and a low-pressure pump, provided fuel in a high-pressure accumulator, from which the fuel stored there is taken from fuel injectors for injection into the associated combustion chambers of an internal combustion engine.
  • the supply of the fuel to a pump working chamber 35 via an electro-magnetic controllable electrically operated valve 2, wherein the electrically operated valve 2 is explained below, is installed on the high-pressure pump 1.
  • the high-pressure pump 1 has a pump housing 3 with a camshaft space 5.
  • camshaft 7 with a trained example as a double cam cam 9 in.
  • the camshaft 7 is arranged in two on both sides of the cam 9 and as a radial bearing
  • Dist. Deten bearings in the form of a housing arranged in the pump housing 3 camp 11 and a flange stop 13, in a connected to the pump housing 3 flange 15, the camshaft space 5 to the environment tightly closed, stored.
  • the flange 15 has a through opening through which a drive-side end portion 17 of the camshaft 7 protrudes.
  • the drive-side end portion 17 has, for example, a cone on which a drive wheel is placed and secured.
  • the drive wheel is formed for example as a pulley or gear.
  • the drive wheel is driven by the internal combustion engine directly or indirectly, for example via a belt drive or a gear transmission.
  • a tappet guide 19 is further inserted, in which a roller 21 having a roller tappet 23 is inserted.
  • the roller 21 runs on the cam 9 of the camshaft 7 during a rotational movement of the same and the roller tappet 23 is thus in the tappet guide 19 translationally moved up and down.
  • the roller tappet 23 cooperates with a pump piston 18 which is arranged in a bore formed in a pump cylinder head 27 cylinder 29 also translationally movable up and down.
  • a follower spring 33 is arranged, which is supported on the one hand to the pump cylinder head 27 and the other part of the roller tappet 23 and a permanent contact of the roller 21 on the cam 9 in the direction of the No ckenwelle 7 ensures.
  • the pump working chamber 35 is formed in extension of the pump piston 18, in which via the electromagnetically controllable electrically operated valve 2 fuel is introduced.
  • the introduction of the fuel takes place during a downward movement of the pump piston 18, while at an upward movement of the pump piston 18 in the pump chamber 35 befindaji fuel via a high-pressure outlet 39 with an inserted outlet valve 16 via a further high-pressure line is conveyed into the high-pressure accumulator.
  • the high pressure pump 1 is lubricated in the total fuel, wherein the fuel is conveyed by the low pressure system in the camshaft space 5, which is fluidly connected to the electrically operated valve 2. This electrically operated valve 2 and its funcionality will be described below.
  • the electromagnetically controllable electrically operated valve 2 is opened and a connection of the pumping work space 35 made with a fuel inlet, so that the pump work chamber 35 via the electrically operated valve 2 fuel is supplied.
  • the high-pressure pump 1 of the pump chamber 35 supplied fuel is compressed and fed via the angeord in the high-pressure outlet 39 angeord designated exhaust valve 16 a high-pressure accumulator (not shown).
  • the electrically operated valve 2 is closed when fuel delivery is to take place, and seals the pump working space 35 from above the fuel supply.
  • the illustrated in Fig. 2, attached to the high pressure pump 1 electrically actuated ended valve 2, has a piston-shaped valve member 14.
  • the piston-shaped valve element 14 has a shaft 25, in particular a cylindrically shaped th shaft 25, and an enlarged head 34.
  • the Pumpenzy cylinder head 27 in the contact area to the closed valve member 14 has a Ven tilsitz 36.
  • the piston-shaped valve element 14 is guided over the shaft 25 in a bore 38 in the pump cylinder head 27 and has the diameter in diam over the shaft 25 enlarged head 34.
  • a sealing surface 37 is formed, which comes into the closed position of the valve element 14 to the valve seat 36 in the pump cylinder head 27 to the plant.
  • the elements of an electric actuator group 41 Darge also: This has a magnetic armature 10 with a cylindrical outer contour and a first central bore 32, wherein the first central bore 32 extends in the direction of a longitudinal axis 45.
  • a first compression spring 4 also protrudes into this first central bore 32 of the armature 10, which has an axial Force on the armature 10 to the valve element 14 in the direction of the longitudinal axis 45 toward out, wherein the longitudinal axis 45 extends parallel to the axis of the opening and closing movement of the valve element 14.
  • the first compression spring 4 protrudes in the direction of the longitudinal axis 45 into a second central bore 50, which is located in a pole core 26.
  • the pole core 26 has a cylindrical outer contour.
  • the armature 10 is also stroke movable in a valve body 40 in a direction of movement Rich V out, with a stop plate 20 is in the axial direction between the valve body 40 and the armature 10.
  • the armature 10 On the Ventilele element 14 side facing away from the armature 10 is on the first compression spring 4 in abutment, the armature 10 is axially movable by an electromagnetic Ansteue tion.
  • the magnet armature 10 is supported in its initial position in the axial direction on its side facing the valve element 14 side on the valve body 40 from.
  • the magnet armature 10 there is a sliding layer 22 between the magnet armature 10 and the valve body 40, wherein the sliding layer 22 extends radially circumferentially about the longitudinal axis 45 between the armature 10 and the valve body 40.
  • the magnet armature 10 surrounds a magnetic coil 6, which forms a magnetic field when energized and thus can exert a magnetic force on the magnet armature 10.
  • the armature 10 moves against the force of a second compression spring 12 away from the valve member 14 to close a working air gap 28, the det between the armature 10 and the pole core 26 det det.
  • valve member 14 is in contact with the armature 10, wherein both elements are not connected to each other in the axial direction, but are held together only by magnetic forces and spring forces in abutment.
  • the piston-shaped valve element 14 is also acted upon in the closing direction by the spring force of the second compression spring 12.
  • the first compression spring 4 acts on the armature 10 and ensures in the de-energized state that the armature 10 acts on the Ventilele element 14 and holds it in the open position. Although this acts against the second compression spring 12, but since the first compression spring 4 has a higher spring force, the valve element 14 is held in the open state. By moving away the armature 10 loses the frictional contact with the valve element 14 whereby the valve element 14 by the force of the second Compression spring 12 moves toward the closed state. In a fully closed state of the valve element 14, the latter is in contact with the sealing surface 37 on the valve seat 36 and seals off the pump working space 35.
  • the pole core 26 is connected via a connecting sleeve 44 with the valve body 40.
  • the connecting sleeve 44 is on the one hand plugged onto a portion of the outer diameter of the valve body 40, which faces the pole core 26, on the other hand, the connecting sleeve 44 is attached to a portion of the outer diameter of the pole core 26 and the Ver connecting sleeve 44 is welded to both components 40, 26 .
  • the connecting sleeve 44 is made of a non-magnetic material.
  • the electrically operated valve 2 has a housing 42, which may be formed in particular as a magnetic sleeve 42.
  • This housing 42 surrounds an electrical actuator group 41 and is held by means of a fastening element 8, which may be designed in particular as a union nut 8, via the valve body 40 with the pump cylinder head 27 in the direction of the longitudinal axis 45 investment.
  • the fastening element 8 has an internal thread 24, whereby the fastening element 8 can be screwed to the pump cylinder head 27.
  • the pump cylinder head 27 forms a cylindrical projection 43 in the direction of the longitudinal axis 45.
  • the valve body 40 is located within this cylindrical projection 43.
  • the cylindrical projection 43 on its outer diameter on an external thread 52 to which the fastening can be screwed fastening element 8 with the internal thread 24. Since the housing 42 surrounds the electric actuator group 41 by the use of the fastener 8 and the electric actuator group 41 in the direction of the longitudinal axis 45 on the pump cylinder head 27 held in abutment without further white components are necessary.
  • the housing 42 has an outwardly ra ing circumferential annular collar 48 and the fastener 8 has egg nen inwardly projecting circumferential collar 46, wherein the annular collar 48 in radial direction away from the longitudinal axis 45 and the collar 46 extends in radial direction to the longitudinal axis 45 towards 45.
  • Fig. 3 is a detail of the electrically operated valve 2 in an enlarged Dar position according to a first embodiment shown.
  • the magnet armature 10 is covered at least approximately completely by the sliding layer 22 on an outer circumference 49 remote from the longitudinal axis 45, wherein the sliding layer 22 is positively and / or materially connected to the magnet armature 10.
  • the sliding layer 22 may be embodied in an exemplary embodiment as a guide sleeve 22, wherein the guide sleeve 22 may be made of a friction-reducing and / or low-friction material.
  • the guide sleeve 22 and / or sliding layer 22 used a faster and improved response and / or switching of the electrically operated valve 2 at a current to the electric actuator group 41, in particular, the magnetic coil 6, can be achieved.
  • the Füh approximately sleeve 22 may have self-lubricating properties, in particular by the use of carbon and / or graphite.
  • the sliding layer 22 and / or guide sleeve 22 moves with the armature 10 hubbeweglich up and down in the direction of the longitudinal axis 45, wherein the force applied to the armature sliding layer 22 and / or guide sleeve 22 in the up and down movement of egg ner inner surface 49 of Valve body 40 slides past.
  • the sliding friction factor is reduced, that is, less force is required to move the magnetic anchor 10 with the sliding layer 22 and / or guide sleeve 22 in the valve body 40 in the direction of the longitudinal axis 45, since the friction between the Mag netanker 10 and the Valve body 40 is reduced, for example, by the advantageous surface structure of the sliding layer 22 and / or guide sleeve 22nd and / or for example by the lubricating properties of the sliding layer 22 and / or guide sleeve 22nd
  • the material of the guide sleeve 22 may have a higher strength and / or hardness compared to the material of the armature 10 and / or the Ven til stressess 40, whereby a longer life of the electrically actu th valve 2 can be achieved.
  • a section of the electrically operated valve 2 is shown in an enlarged Dar position according to a second embodiment.
  • the Ven til stresses 40 on the longitudinal axis 45 facing inner surface 51 is at least partially or almost completely covered by the sliding layer 22, wherein the sliding layer 22 is non-positively and / or materially connected to the valve body 40.
  • the sliding layer 22 or the guide sleeve 22 may be connected by means of a variety of mounting measures or fastening measures or joining measures with the armature 10 or the valve body 40 and / or be introduced.
  • an adhesive method or a screwing procedure or a joining method by means of press-fitting, in particular by means of a press fit can be used for this purpose or a combination of such measures.
  • the least one guide sleeve 22 is 29welst with the valve body 40 and / or the armature 10, in particular by means of friction welding, and thus forms a cohesive and / or non-positive connection.
  • the guide sleeve 22 and / or the magnet armature 10 and / or the valve body 40 are set in rotation, before the two parts are connected to one another.
  • the guide sleeve 22 is thermally treated prior to installation, in particular special heated, that the inner diameter of the guide sleeve 22 reversibly and temporarily limited increases, which days after the successful Mon the guide sleeve 22nd on the magnet armature 10 reduces the inner diameter of the guide sleeve and thereby forms a frictional connection with the outer periphery 49 of the armature 10, in particular by means of a Surface pressure.
  • the guide sleeve 22 through the thermal loading treatment in the same process step additionally experienced an increase in the strength and / or hardness of the material of the guide sleeve 22 / obtained.
  • the guide sleeve 22 is thermally treated prior to assembly, in particular cooled, that the Au # mismesser the guide sleeve 22 reversible and temporarily limited verklei nert, which is after the successful assembly of the guide sleeve 22 in the interior surface 51 of the valve body 40, the outer diameter of the guide sleeve 22 increases and thereby forms a frictional connection with the inner surface 51 of the valve body 40, in particular by means of a surface pressure.
  • Magnetic anchor 10 and / or on the inner surface 51 of the valve body 40 be introduced.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape (2) à actionnement électrique, en particulier dans une pompe à haute pression (1) d'un système d'injection de carburant, qui possède un élément de soupape (14) pouvant se déplacer entre une position ouverte et une position fermée dans la direction d'un axe longitudinal (45), comprenant une armature magnétique (10) qui est en contact mécanique avec l'élément de soupape (14) dans la direction axiale et qui prend appui, sur sa face opposée à l'élément de soupape (14), contre un premier ressort de compression (4). L'armature magnétique (10) peut être déplacée par une excitation électromagnétique et l'armature magnétique (10) est guidée en va-et-vient dans un corps de soupape (40) dans la direction de l'axe longitudinal (45). Selon l'invention, une couche de glissement (22) se trouve ici entre l'armature magnétique (10) et le corps de soupape (40). La couche de glissement (22) s'étend circonférentiellement dans le sens radial autour de l'axe longitudinal (45) entre l'armature magnétique (10) et le corps de soupape (40).
PCT/EP2018/081829 2017-12-18 2018-11-20 Soupape, en particulier soupape d'aspiration, dans une pompe à haute pression d'un système d'injection de carburant WO2019120822A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017222985.3A DE102017222985A1 (de) 2017-12-18 2017-12-18 Ventil, insbesondere Saugventil,in einer Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102017222985.3 2017-12-18

Publications (1)

Publication Number Publication Date
WO2019120822A1 true WO2019120822A1 (fr) 2019-06-27

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Application Number Title Priority Date Filing Date
PCT/EP2018/081829 WO2019120822A1 (fr) 2017-12-18 2018-11-20 Soupape, en particulier soupape d'aspiration, dans une pompe à haute pression d'un système d'injection de carburant

Country Status (2)

Country Link
DE (1) DE102017222985A1 (fr)
WO (1) WO2019120822A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3016993A1 (de) * 1979-05-10 1980-11-20 Gen Motors Corp Elektromagnetische kraftstoffeinspritzeinrichtung
EP2628941A1 (fr) * 2012-02-15 2013-08-21 Robert Bosch Gmbh Soupape d'injection de combustible
DE102014214811A1 (de) 2014-07-29 2016-02-04 Robert Bosch Gmbh Hochdruckpumpe
WO2016150607A1 (fr) * 2015-03-25 2016-09-29 Robert Bosch Gmbh Soupape de commande de débit à actionnement électromagnétique, en particulier destinée à commander le débit de refoulement d'une pompe à carburant haute pression
DE102016205889A1 (de) * 2016-04-08 2017-10-12 Robert Bosch Gmbh Elektromagnetisch betätigbares Saugventil

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010061219B4 (de) * 2010-12-14 2015-06-11 Hilite Germany Gmbh Elektromagnetisches Stellglied
DE102014207988B3 (de) * 2014-04-29 2015-09-10 Schaeffler Technologies AG & Co. KG Elektromagnetische Stellvorrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3016993A1 (de) * 1979-05-10 1980-11-20 Gen Motors Corp Elektromagnetische kraftstoffeinspritzeinrichtung
EP2628941A1 (fr) * 2012-02-15 2013-08-21 Robert Bosch Gmbh Soupape d'injection de combustible
DE102014214811A1 (de) 2014-07-29 2016-02-04 Robert Bosch Gmbh Hochdruckpumpe
WO2016150607A1 (fr) * 2015-03-25 2016-09-29 Robert Bosch Gmbh Soupape de commande de débit à actionnement électromagnétique, en particulier destinée à commander le débit de refoulement d'une pompe à carburant haute pression
DE102016205889A1 (de) * 2016-04-08 2017-10-12 Robert Bosch Gmbh Elektromagnetisch betätigbares Saugventil

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