EP3036430B1 - Device for a high-pressure pump for a motor vehicle - Google Patents

Device for a high-pressure pump for a motor vehicle Download PDF

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Publication number
EP3036430B1
EP3036430B1 EP15733401.2A EP15733401A EP3036430B1 EP 3036430 B1 EP3036430 B1 EP 3036430B1 EP 15733401 A EP15733401 A EP 15733401A EP 3036430 B1 EP3036430 B1 EP 3036430B1
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EP
European Patent Office
Prior art keywords
actuator
actuator assembly
valve
volume body
fluid
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.)
Not-in-force
Application number
EP15733401.2A
Other languages
German (de)
French (fr)
Other versions
EP3036430A1 (en
Inventor
Burhan Dagdelen
Andreas Mühlbauer
Rainer Weber
Stephan BIAS
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
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Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP3036430A1 publication Critical patent/EP3036430A1/en
Application granted granted Critical
Publication of EP3036430B1 publication Critical patent/EP3036430B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/20—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
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • 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
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the present invention relates to a device for a high-pressure pump for a motor vehicle, which is adapted to minimize vibration and noise developments through valves.
  • solenoid actuated valves are used to control fluid flow. These valves are usually adjusted in the axial direction to adjust a flow area and provide a required amount of fluid, especially fuel. This move moving components due to space limitations on elements that are deliberately introduced constructive, for example, to limit a stroke of the moving parts of the valve. Due to the impact of moving components on immovable rigidly arranged components of the valve, a pulse is transmitted, which leads to vibrations and scattered over the high-pressure pump can be reproduced as sound and possibly perceived as disturbing noise.
  • EP 0 195 261 A2 discloses a solenoid valve for fuel injection systems, which is used to measure the injection quantity and to control the injection timing.
  • the solenoid valve has in a valve housing an electromagnet and actuated by this valve closing part, which cooperates with a fixed valve seat.
  • a valve closing part open towards the damping chamber is arranged at the stop, the surrounding the opening Wall has a very narrow stop surface.
  • valve-closing part fluid When approaching the valve closure member fluid is displaced from the damping chamber in the form of a squish flow between the abutment surface and the head portion of the valve closure member, so that are avoided by the damping generated thereby remindpreller.
  • lifting the valve-closing part fluid can flow through a throttle bore or a check valve in the damping chamber, so that a release of the valve-closing part of the abutment surface with little effort is possible.
  • a metering unit for a fuel pump of a fuel injection system for air-compression, self-igniting internal combustion engine comprises an actuator and a valve body, wherein the valve body is actuated at least indirectly by the actuator.
  • the valve body is in this case actuated by means of a transmission sleeve.
  • the transmission sleeve may consist of a plastic.
  • DE 10 2010 061 793 A1 discloses an electromagnetically actuated quantity control valve for controlling the delivery rate of a high pressure pump.
  • the high-pressure pump has a fluid-filled movement space, a movement part of an electromagnetic actuator arranged therein and a stop. Between the moving part and the stop disk-like intermediate element is preferably arranged.
  • an apparatus for a high-pressure pump for a motor vehicle comprises a valve housing, a central axis and an actuator assembly, which is arranged substantially along the central axis in the valve housing.
  • the actuator assembly in this case has an Aktoraus quietlyung, starting from a first end of the actuator assembly in the Actuator assembly extends.
  • the actuator assembly has at least one hydraulic compensation opening, which penetrates a wall of the actuator assembly from the Aktorausappelung to an outdoor area.
  • the device has a volume body, which is arranged in the AktorausEnglishung spaced from the Aktorbaueau and extending into a region of the at least one hydraulic compensation opening.
  • the volume body is arranged immovably relative to the valve housing, while the Aktorbauè is arranged relative to the central axis relative to the valve housing and axially movable relative to the volume body.
  • a device for a high-pressure pump for a motor vehicle which is adapted during operation of the motor vehicle to keep vibration and noise developments by valves low.
  • a controlled hydraulic damping is achieved during operation of the motor vehicle, which makes it possible to reduce an impulse upon impact of moving components of the valve to adjacent optionally rigidly mounted components, so as to reduce vibrations and noise.
  • the hydraulic damping is achieved by the volume body in the valve housing, which is arranged relative to the valve housing as a non-movable component of the device in the valve housing and selectively changes a cross section and a volume for a fluid flowing through.
  • a fluid in particular a fuel, for example, the high-pressure pump and corresponding valves.
  • a valve is designed according to the claimed device, the flowing fluid passes, for example, into the valve housing and from there through the at least one hydraulic compensation opening in the region of Aktorausappelung.
  • the valve is opened or closed, fluid flows in or out of the actuator recess, allowing hydraulic damping to continue as it progresses.
  • the actuator assembly may be formed as a single element, for example in one piece, or may also comprise a plurality of components, which are, for example, positively, positively and / or materially connected to each other.
  • the described hydraulic damping which is achieved by the claimed device is, as described, achieved by the solid, which is rigidly arranged as an additional component of the valve in the valve housing.
  • Movable components of the device such as the Aktorbaueria, are accordingly not changed in particular. In this way, it is avoided to increase the mass of moving components, which would lead to an increase in momentum when these components move.
  • the volume body as a rigidly arranged component of the valve, it is simply possible to passively achieve a hydraulic damping of the fluid flowing through, without having to actively set, for example, a hydraulic damping.
  • Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that an actuator is energized and counter-energized in order to to mitigate such an impact on neighboring components. This inevitably requires additional electrical power and leads to an increased consumption of the motor vehicle, which is avoided for example by means of the device described.
  • a number of the hydraulic compensation opening is not limited to one and can be scaled arbitrarily in this context, so that the at least one or more hydraulic compensation openings penetrate the wall of the actuator assembly and connect the Aktoraus originallyung with the outer region of the actuator assembly.
  • a geometry of the at least one hydraulic compensation opening is variable and can be formed due to space constraints. For example, it is advantageous if a plurality of hydraulic equalization holes are drilled in the wall of the actuator assembly.
  • a geometry of the volume body is arbitrarily scalable due to space constraints, so that at least ensures that the volume is spaced from the movable components of the valve and during operation of the motor vehicle not in contact with them and that there is a controlled change in the volume of the Fluid is flowed through.
  • a plurality of solids are arranged in the valve housing or Aktoraus brieflyung that meet the functions just described.
  • the actuator assembly comprises an actuator and a valve needle which, in an operating state in cooperation with a sealing seat, prevents and otherwise releases a fluid flow of a fluid in a closing position of the actuator assembly.
  • the actuator of the actuator assembly on the Aktorausströmung and the at least one hydraulic compensation opening is formed substantially between the actuator and the valve needle.
  • the volume body is arranged in the Aktoraus quietlyung spaced from the actuator and protrudes in an opening or closing process in the region of the at least one hydraulic compensation opening, so that, for example, the moving valve needle of the actuator assembly approaches the solid or away from it.
  • the actuator of the actuator assembly includes, for example, an anchor or can also be called an anchor itself.
  • the first aspect of the solid body is formed substantially cylindrical.
  • the volume body is designed rotationally symmetrical, which allows, for example, in connection with a fluid flowing through during operation of the motor vehicle, a homogeneous flow pattern and thereby a controlled hydraulic damping.
  • the solid body extends substantially along the central axis or is arranged at least substantially parallel to the middle axis.
  • a rotationally symmetrical structure of the device is made possible, which allows a preferred embodiment of the valve with hydraulic damping.
  • the device comprises a pole piece, which is arranged adjacent to the actuator of the actuator assembly and by means of which the actuator assembly is magnetically openable or closable.
  • the volume body extends substantially from the first end of the actuator assembly into the region of the at least one hydraulic compensation opening.
  • a magnetically actuated valve for controlling the fluid flow in which a controlled hydraulic damping of the flowing fluid and the moving components of the valve is achieved by the arranged volume.
  • the moving actuator assembly with the actuator encounters the adjacent pole piece causing a momentum transfer, thus resulting in vibration and noise.
  • the momentum transfer By means of the volume of the impact is damped and reduced the momentum transfer, which counteracts as a result of the formation of vibration and noise.
  • first aspect of the solid is cohesively and / or non-positively and / or positively coupled to the pole piece.
  • This embodiment of the device shows ways in which the solid body can be arranged rigidly and immovably in the valve housing.
  • the volume body and the pole piece are welded together, glued or clamped and so together immovably arranged in the valve housing, while the actuator and the valve needle of the actuator assembly are arranged axially movable in the valve housing relative to the volume body and the pole piece.
  • the pole piece has a PolausEnglishung in which the solid is partially arranged.
  • the first aspect of the solid body is formed integrally with the pole piece.
  • a high-pressure pump comprises a device according to the first aspect.
  • FIG. 1 schematically shows a high-pressure pump 30, which has, inter alia, a fluid supply line 33.
  • the fluid supply line 33 is hydraulically coupled to a cylinder space 31.
  • the high-pressure pump 30 also has a fluid drain 35.
  • the cylinder chamber 1 is arranged hydraulically between the fluid supply line 33 and the fluid discharge line 35.
  • the high-pressure pump 30 is in particular a high-pressure pump for a fuel injection system for internal combustion engines of motor vehicles.
  • a pump housing 32 of the high pressure pump 30 surrounds the cylinder chamber 1 and the fluid supply line 33 to the cylinder chamber 31, and the fluid discharge 35.
  • fluid is sucked through the fluid supply line 33 into the cylinder chamber 31 from a low pressure region.
  • the fluid supply line 33 is hydraulically coupled by means of a prefeed pump (not explicitly shown) to a fluid tank (not explicitly shown).
  • a valve 1 is arranged, which controls an inlet of the fluid into the cylinder chamber 31.
  • the fluid in the cylinder chamber 31 is subjected to a pressure, for example by a piston movement in the cylinder chamber.
  • the pressurized fluid is discharged from the cylinder chamber 31 through an outlet valve by means of the fluid discharge 35 from the high-pressure pump 30.
  • the fluid discharge line 35 is coupled to a rail of a common rail injection system.
  • the high pressure pump 30 is configured, for example, pressures of up to 2000 bar or more provide.
  • the high-pressure pump 30 is a piston pump, but the high-pressure pump can also have a different design.
  • FIGS. 2A and 2B show in a cross section an exemplary construction of the valve 1 which is magnetically actuated and which comprises a valve housing 3, a central axis 17 and an actuator assembly 5.
  • the Aktorbauxx 5 is relative to the central axis 17 in the valve housing 3 axially movable relative to the valve housing 3 and in this embodiment has an actuator 7 and a valve needle 9, which during operation of the valve 1 in cooperation with a sealing seat 16, a fluid flow a fluid in a closed position of the actuator assembly 5, consisting of actuator 7 and valve needle 9, prevents and otherwise releases.
  • the actuator 7 of the actuator assembly 5 includes, for example, an armature or may itself be referred to as an anchor.
  • a pole piece 21 and a spring 19 are arranged, which realize an opening and closing process of the valve 1.
  • the spring 19 exerts a spring force on the actuator assembly 5 and thereby pushes the actuator 7 of the actuator assembly 5 away from the pole piece 21. Without energizing the pole piece 21, ie without applying a voltage to a magnetic coil 211, which is wound around the pole piece 21, the valve 1 is thus permanently open.
  • valve 1 If the pole piece 21, that is, the winding coil 211 is energized, a magnetic closing of the valve 1 is made possible by a magnetic force generated by the energization of the pole piece 21 outweighs the spring force and accelerates the actuator 7 of the actuator assembly 5 in the direction of the pole piece 21 ,
  • magnetically actuated valves for example, whether they are normally open or normally closed.
  • the valve 1 described here is, as already described, normally open. In further embodiments, the valve 1 may also be designed so that it is normally closed.
  • the actuator 7 of the actuator assembly 5 has, in the region of a first end 6 of the actuator assembly 5, an actuator recess 11 which extends into the actuator assembly 5 and in which, inter alia, part of the spring 19 is arranged.
  • the pole piece 21 has a Polaus spiritung 23, in which the spring 19 extends. Between the actuator 7 and the valve needle 9 hydraulic compensation openings 13 are formed, which allow the fluid flow from an outer region 12 of the actuator assembly 5 in the Aktorausströmung 11 during operation of the valve 1.
  • a volume body 15 is arranged, which extends into a region 14 of the hydraulic compensation openings 13.
  • the volume body 15 is, for example, positively connected to the pole piece 21 and, for example, was pressed into the pole piece 21 as part of a production process.
  • the volume body 15 is essentially cylindrical and has a wider cylindrical body in the pole recess 23 and a narrower cylindrical body in the form of a pin in the actuator recess 11.
  • the solid 15 may have other geometric shapes.
  • FIG. 2B the area 14 of the hydraulic compensation openings 13 of the valve 1 is shown in detail.
  • a part of the actuator assembly 5 and the actuator 7 and the valve needle 9 is shown enlarged.
  • the fluid for example a fuel
  • the fluid flows into the valve 1 and the valve housing 3 and reaches the area 14 of the hydraulic compensation openings 13.
  • the fluid flows through the hydraulic compensation openings 13 and thus enters the Aktoraus originallyung 11 of the actuator 7 of the actuator assembly 5.
  • the fluid flows around the volume body 15 and the spring 19, so that a flow pattern of the fluid is influenced by the volume body 15.
  • the volume body 15 changes a volume accessible to the fluid in the region 14 of the hydraulic compensation openings 13, so that a controlled hydraulic damping of the fluid and the moving components of the valve 1 is achieved.
  • a stroke 10 is present between the pole piece 21 and the actuator 7 of the actuator assembly 5, which is formed for example in a design of the valve 1 predetermined.
  • the volume body 15 does not protrude into the area of the hydraulic compensation openings 13 and thereby does not influence the cross section and the volume of the hydraulic compensation openings 13 for the fluid flowing through.
  • the hub 10 between the pole piece 21 and the actuator 7 is closed by the pole piece 21 is energized and outweighs the magnetic force generated thereby acting through the spring 19 spring force. In this case, fluid is pressed out of the actuator recess 11 through the hydraulic compensation bores 13 and thus arrives in the outer region 12 of the actuator assembly 5.
  • FIG. 3A shows the valve 1 in a cross section in the closed position in which the volume body 15 projects into the region 14 of the hydraulic compensation openings 13.
  • the volume 15 has the Cross-section and the volume in the region 14 of the hydraulic equalization openings 13 changed and thereby specifically influences an outflow of the fluid from the Aktorausappelung 11.
  • the fluid flowing through has less volume when it flows out of the actuator recess 11 through the hydraulic compensation openings 13, so that the movement of the actuator assembly 5 is influenced by a throttled movement of the fluid.
  • FIG. 3B shows that in FIG. 3A illustrated valve 1 in the closed position with a detailed view of the area 14 of the hydraulic compensation openings 13.
  • the volume body 15 projects in contrast to the position FIGS. 2A and 2B with one end into the region 14 of the hydraulic compensation openings 13 purely and thereby changes the volume accessible to the fluid flowing through.
  • This volume change has a corresponding effect on a subsequent opening process of the valve 1, so that due to the volume body 15, for example, the movement of the valve needle 9 is attenuated when opening the valve 1 for the reasons described and the impact force and the momentum transfer are reduced.
  • valve 1 thus allows in a simple manner by the rigidly arranged volume body 15, a hydraulic damping of the moving Components of the valve 1, such as the actuator 7 and the valve needle 9 of the actuator assembly 5 in an opening and closing process of the valve 1.
  • movably arranged components of the valve 1 are not changed, so that, for example, a mass of the actuator assembly. 5 remains unchanged.
  • An arrangement of the volume body 15, for example, on the actuator assembly 5 may also lead to a damping of movement of the actuator assembly 5, but also due to the increase in the mass moved to an increased pulse, which in turn reduces the effect of a desired hydraulic damping. By the described embodiments, such interaction is bypassed.
  • the hydraulic damping by means of the volume body 15 is achieved substantially passive, since the volume body 15 is arranged as a rigid component of the valve 1 immovable, for example, relative to the valve housing 3.
  • Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that the pole piece 21 is energized and counter-energized so as to attenuate the impact of the actuator 7 on the pole piece 21 or the impact of the valve needle 9 against the valve housing 3. This inevitably requires additional electrical power and leads to increased consumption of the motor vehicle.
  • a further beneficial effect is achieved, characterized in that the spring 19 is arranged around the volume body 15.
  • the volume body 15 has in this way also a spring-guiding effect, since the spring 19 is guided on an inner diameter of the volume body 15.
  • a number of the hydraulic compensation openings 13 is not limited and can be arbitrary in this context are scaled, so that the at least one or more hydraulic compensation openings 13 penetrate the wall of the actuator assembly 5 and connect the Aktoraus originallyung 11 with the outer region 12 of the actuator assembly 5.
  • a geometry of the at least one hydraulic compensation opening 13 is variable and can be formed due to space constraints. For example, it is advantageous if a plurality of hydraulic compensation openings 13 are drilled through the wall of the actuator assembly 5.
  • a geometry of the volume body 15 is arbitrarily scalable due to space constraints, so that at least ensures that the volume body 15 is spaced from movable components of the valve 1, such as the actuator 7 and the valve needle 9 of the actuator assembly 5, and not during operation of the motor vehicle get in contact with them.
  • the volume body 15 always carries out a controlled change in the volume in the region 14 of the hydraulic compensation openings 13, through which the fluid flows during operation of the motor vehicle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die vorliegende Erfindung betrifft eine Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug, die dazu geeignet ist, Vibrationen und Geräuschentwicklungen durch Ventile gering zu halten.The present invention relates to a device for a high-pressure pump for a motor vehicle, which is adapted to minimize vibration and noise developments through valves.

Bei einem Einsatz von Hochdruckpumpen in Kraftfahrzeugen werden zum Beispiel durch Magnete betätigte Ventile zur Steuerung eines Fluidflusses verwendet. Diese Ventile werden gewöhnlich in axialer Richtung verstellt, um einen Strömungsquerschnitt einzustellen und eine benötigte Menge eines Fluids, insbesondere Kraftstoff, bereitzustellen. Dabei stoßen bewegte Bauteile bauraumbedingt an begrenzende Elemente, die zum Beispiel bewusst konstruktiv eingebracht sind, um einen Hub der beweglichen Bauteile des Ventils zu begrenzen. Durch das Auftreffen bewegter Bauteile auf unbewegliche starr angeordnete Bauteile des Ventils wird ein Impuls übertragen, welcher zu Vibrationen führt und über die Hochdruckpumpe verstreut als Schall widergegeben werden kann und gegebenenfalls als störendes Geräusch wahrgenommen wird.For example, when using high pressure pumps in automobiles, solenoid actuated valves are used to control fluid flow. These valves are usually adjusted in the axial direction to adjust a flow area and provide a required amount of fluid, especially fuel. This move moving components due to space limitations on elements that are deliberately introduced constructive, for example, to limit a stroke of the moving parts of the valve. Due to the impact of moving components on immovable rigidly arranged components of the valve, a pulse is transmitted, which leads to vibrations and scattered over the high-pressure pump can be reproduced as sound and possibly perceived as disturbing noise.

EP 0 195 261 A2 offenbart ein Magnetventil für Kraftstoffeinspritzanlagen, das zum Bemessen der Einspritzmenge und zum Steuern des Einspritzzeitpunktes dient. Das Magnetventil hat in einem Ventilgehäuse einen Elektromagneten und ein von diesem betätigtes Ventilschließteil, das mit einem festen Ventilsitz zusammenwirkt. Zum Dämpfen der Öffnungsbewegung des Ventilschließteils gegen einen festen Anschlag und zum Niedrighalten der hydraulischen Klebekräfte zwischen dem ventilschließteil und dem Anschlag, ist am Anschlag eine zum Ventilschließteil hin offene Dämpfungskammer angeordnet, deren die Öffnung umgebende Wand eine sehr schmale Anschlagfläche hat. Beim Annähern des Ventilschließglieds wird aus der Dämpfungskammer Fluid in Form einer Quetschströmung zwischen der Anschlagfläche und dem Kopfteil des Ventilschließteils verdrängt, so dass durch die dadurch erzeugte Dämpfung Rückpreller vermieden werden. Beim Abheben des Ventilschließteils kann Fluid durch eine Drosselbohrung oder ein Rückschlagventil in die Dämpfungskammer fließen, so dass ein Lösen des Ventilschließteils von der Anschlagfläche mit geringem Kraftaufwand möglich ist. EP 0 195 261 A2 discloses a solenoid valve for fuel injection systems, which is used to measure the injection quantity and to control the injection timing. The solenoid valve has in a valve housing an electromagnet and actuated by this valve closing part, which cooperates with a fixed valve seat. To dampen the opening movement of the valve closing member against a fixed stop and to keep low the hydraulic adhesive forces between the valve closing part and the stop, a valve closing part open towards the damping chamber is arranged at the stop, the surrounding the opening Wall has a very narrow stop surface. When approaching the valve closure member fluid is displaced from the damping chamber in the form of a squish flow between the abutment surface and the head portion of the valve closure member, so that are avoided by the damping generated thereby Rückpreller. When lifting the valve-closing part fluid can flow through a throttle bore or a check valve in the damping chamber, so that a release of the valve-closing part of the abutment surface with little effort is possible.

In DE 10 2012 211 394 A1 ist eine Zumesseinheit für eine Brennstoffpumpe einer Brennstoffeinspritzanlage für luftverdichtende, selbstzündende Brennkraftmaschinen beschrieben. Die Zumesseinheit umfasst einen Aktor und einen Ventilkörper, wobei der Ventilkörper zumindest mittelbar von dem Aktor betätigbar ist. Der Ventilkörper ist hierbei mittels einer Übertragungshülse betätigbar. Die Übertragungshülse kann aus einem Kunststoff bestehen.In DE 10 2012 211 394 A1 a metering unit for a fuel pump of a fuel injection system for air-compression, self-igniting internal combustion engine is described. The metering unit comprises an actuator and a valve body, wherein the valve body is actuated at least indirectly by the actuator. The valve body is in this case actuated by means of a transmission sleeve. The transmission sleeve may consist of a plastic.

DE 10 2010 061 793 A1 offenbart ein elektromagnetisch betätigtes Mengensteuerventil zur Steuerung der Fördermenge einer Hochdruckpumpe. Die Hochdruckpumpe besitzt einen mit einem Fluid befüllbaren Bewegungsraum, einem in diesem angeordneten Bewegungsteil einer elektromagnetischen Betätigungseinrichtung und einem Anschlag. Zwischen dem Bewegungsteil und dem Anschlag ist vorzugsweise scheibenartiges Zwischenelement angeordnet. DE 10 2010 061 793 A1 discloses an electromagnetically actuated quantity control valve for controlling the delivery rate of a high pressure pump. The high-pressure pump has a fluid-filled movement space, a movement part of an electromagnetic actuator arranged therein and a stop. Between the moving part and the stop disk-like intermediate element is preferably arranged.

Es ist eine Aufgabe, eine Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug zu schaffen, die geeignet ist, Vibrationen und Geräuschentwicklungen durch Ventile während eines Betriebs eines Kraftfahrzeugs gering zu halten.It is an object to provide an apparatus for a high-pressure pump for a motor vehicle, which is suitable for keeping vibration and noise developments through valves during operation of a motor vehicle low.

Gemäß eines ersten Aspekts der Erfindung umfasst eine Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug ein Ventilgehäuse, eine Mittelachse und eine Aktorbaugruppe, die im Wesentlichen entlang der Mittelachse in dem Ventilgehäuse angeordnet ist. Die Aktorbaugruppe weist dabei eine Aktorausnehmung auf, die sich ausgehend von einem ersten Ende der Aktorbaugruppe in die Aktorbaugruppe erstreckt. Darüber hinaus weist die Aktorbaugruppe mindestens eine hydraulische Ausgleichsöffnung auf, die eine Wandung der Aktorbaugruppe von der Aktorausnehmung bis in einen Außenbereich durchdringt. Außerdem weist die Vorrichtung einen Volumenkörper auf, der in der Aktorausnehmung beabstandet zu der Aktorbaugruppe angeordnet ist und der sich bis in einen Bereich der mindestens einen hydraulischen Ausgleichsöffnung erstreckt. Dabei ist der Volumenkörper relativ zu dem Ventilgehäuse unbeweglich angeordnet, während die Aktorbaugruppe in Bezug auf die Mittelachse relativ zu dem Ventilgehäuse und relativ zu dem Volumenkörper axial beweglich angeordnet ist.According to a first aspect of the invention, an apparatus for a high-pressure pump for a motor vehicle comprises a valve housing, a central axis and an actuator assembly, which is arranged substantially along the central axis in the valve housing. The actuator assembly in this case has an Aktorausnehmung, starting from a first end of the actuator assembly in the Actuator assembly extends. In addition, the actuator assembly has at least one hydraulic compensation opening, which penetrates a wall of the actuator assembly from the Aktorausnehmung to an outdoor area. In addition, the device has a volume body, which is arranged in the Aktorausnehmung spaced from the Aktorbaugruppe and extending into a region of the at least one hydraulic compensation opening. In this case, the volume body is arranged immovably relative to the valve housing, while the Aktorbaugruppe is arranged relative to the central axis relative to the valve housing and axially movable relative to the volume body.

Auf diese Weise wird eine Vorrichtung für eine Hochdruckpumpe für ein Kraftfahrzeug geschaffen, die dazu geeignet ist, während eines Betriebs des Kraftfahrzeugs, Vibrationen und Geräuschentwicklungen durch Ventile gering zu halten. Durch die beschriebene Vorrichtung wird während des Betriebs des Kraftfahrzeugs eine kontrollierte hydraulische Dämpfung erreicht, die es ermöglicht, einen Impuls beim Auftreffen bewegter Bauteile des Ventils auf benachbarte gegebenenfalls starr angebrachte Bauteile zu reduzieren, um so Vibrationen und Geräuschentwicklungen zu verringern. Konkret wird die hydraulische Dämpfung durch den Volumenkörper in dem Ventilgehäuse erreicht, welcher relativ zu dem Ventilgehäuse als nicht bewegliches Bauteil der Vorrichtung in dem Ventilgehäuse angeordnet ist und gezielt einen Querschnitt und ein Volumen für ein durchströmendes Fluid verändert.In this way, a device for a high-pressure pump for a motor vehicle is provided, which is adapted during operation of the motor vehicle to keep vibration and noise developments by valves low. By the described device, a controlled hydraulic damping is achieved during operation of the motor vehicle, which makes it possible to reduce an impulse upon impact of moving components of the valve to adjacent optionally rigidly mounted components, so as to reduce vibrations and noise. Specifically, the hydraulic damping is achieved by the volume body in the valve housing, which is arranged relative to the valve housing as a non-movable component of the device in the valve housing and selectively changes a cross section and a volume for a fluid flowing through.

Im Rahmen eines Betriebs des Kraftfahrzeugs durchströmt ein Fluid, insbesondere ein Kraftstoff, zum Beispiel die Hochdruckpumpe und entsprechende Ventile. Ist ein Ventil entsprechend der beanspruchten Vorrichtung ausgestaltet, gelangt das strömende Fluid zum Beispiel in das Ventilgehäuse und von dort durch die mindestens eine hydraulische Ausgleichsöffnung in den Bereich der Aktorausnehmung. Bei einem Öffnen oder Schließen des Ventils fließt Fluid in die Aktorausnehmung herein oder aus dieser heraus und ermöglicht so im weiteren Verlauf eine hydraulische Dämpfung.As part of an operation of the motor vehicle flows through a fluid, in particular a fuel, for example, the high-pressure pump and corresponding valves. If a valve is designed according to the claimed device, the flowing fluid passes, for example, into the valve housing and from there through the at least one hydraulic compensation opening in the region of Aktorausnehmung. When the valve is opened or closed, fluid flows in or out of the actuator recess, allowing hydraulic damping to continue as it progresses.

In diesem Zusammenhang wird durch den gezielten Einbau des Volumenkörpers in dem Bereich der Aktorausnehmung ein Volumen, das das Fluid durchströmt, kontrolliert verändert und so eine hydraulische Dämpfung der bewegten Aktorbaugruppe erreicht. Auf diese Weise werden eine Aufschlagskraft und ein Impulsübertrag der bewegten Aktorbaugruppe auf benachbarte Bauteile des Ventils verringert. Folglich werden einer Entstehung von Vibrationen und einer Entwicklung von Geräuschen während des Betriebs des Ventils entgegengewirkt. Die Aktorbaugruppe kann dabei als ein einzelnes Element, zum Beispiel einstückig, ausgebildet sein oder auch mehrere Bauteile umfassen, die beispielsweise form-, kraft- und/oder stoffschlüssig miteinander verbunden sind.In this context, by the targeted installation of the volume body in the area of Aktorausnehmung a volume that flows through the fluid, controlled changes and thus achieves a hydraulic damping of the moving actuator assembly. In this way, a impact force and a momentum transfer of the moving actuator assembly are reduced to adjacent components of the valve. Consequently, generation of vibrations and development of noise during operation of the valve are counteracted. The actuator assembly may be formed as a single element, for example in one piece, or may also comprise a plurality of components, which are, for example, positively, positively and / or materially connected to each other.

Die beschriebene hydraulische Dämpfung, die durch die beanspruchte Vorrichtung erreicht wird, wird, wie beschrieben, durch den Volumenkörper erzielt, der als zusätzliches Bauteil des Ventils in dem Ventilgehäuse starr angeordnet ist. Bewegliche Bauteile der Vorrichtung, wie zum Beispiel die Aktorbaugruppe, werden dementsprechend insbesondere nicht verändert. Auf diese Weise wird vermieden, die Masse von bewegten Bauteilen zu erhöhen, was bei einer Bewegung dieser Bauteile zu einem erhöhten Impuls führen würde. Außerdem ist es mit dem Volumenkörper als starr angeordnetes Bauteil des Ventils einfach möglich, eine hydraulische Dämpfung des durchströmenden Fluids im Wesentlichen passiv zu erzielen, ohne beispielsweise eine hydraulische Dämpfung aktiv einstellen zu müssen. Eine aktive hydraulische Dämpfung wird beispielsweise bei einem Magnetventil dadurch erzielt, dass ein Aktuator bestromt und gegenbestromt wird, um so ein Auftreffen auf benachbarte Komponenten abzuschwächen. Dies benötigt zwangsläufig zusätzliche elektrische Leistung und führt zu einem erhöhten Verbrauch des Kraftfahrzeugs, was zum Beispiel mittels der beschriebenen Vorrichtung vermieden wird.The described hydraulic damping, which is achieved by the claimed device is, as described, achieved by the solid, which is rigidly arranged as an additional component of the valve in the valve housing. Movable components of the device, such as the Aktorbaugruppe, are accordingly not changed in particular. In this way, it is avoided to increase the mass of moving components, which would lead to an increase in momentum when these components move. Moreover, with the volume body as a rigidly arranged component of the valve, it is simply possible to passively achieve a hydraulic damping of the fluid flowing through, without having to actively set, for example, a hydraulic damping. Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that an actuator is energized and counter-energized in order to to mitigate such an impact on neighboring components. This inevitably requires additional electrical power and leads to an increased consumption of the motor vehicle, which is avoided for example by means of the device described.

Eine Anzahl der hydraulischen Ausgleichsöffnung ist nicht auf eins beschränkt und kann in diesem Zusammenhang beliebig skaliert werden, sodass die mindestens eine oder mehreren hydraulischen Ausgleichsöffnungen die Wandung der Aktorbaugruppe durchdringen und die Aktorausnehmung mit dem Außenbereich der Aktorbaugruppe verbinden. Außerdem ist auch eine Geometrie der mindestens einen hydraulischen Ausgleichsöffnung variabel und kann bauraumbedingt ausgebildet werden. Zum Beispiel ist es vorteilhaft, wenn mehrere hydraulische Ausgleichsöffnungen in die Wandung der Aktorbaugruppe gebohrt werden.A number of the hydraulic compensation opening is not limited to one and can be scaled arbitrarily in this context, so that the at least one or more hydraulic compensation openings penetrate the wall of the actuator assembly and connect the Aktorausnehmung with the outer region of the actuator assembly. In addition, a geometry of the at least one hydraulic compensation opening is variable and can be formed due to space constraints. For example, it is advantageous if a plurality of hydraulic equalization holes are drilled in the wall of the actuator assembly.

Auch eine Geometrie des Volumenkörpers ist bauraumbedingt beliebig skalierbar, sodass zumindest gewährleistet wird, dass der Volumenkörper beabstandet zu beweglichen Bauteilen des Ventils angeordnet ist und während eines Betriebs des Kraftfahrzeugs nicht mit diesen in Kontakt gerät und dass eine kontrollierte Veränderung des Volumens erfolgt, das von dem Fluid durchströmt wird. Darüber hinaus ist es auch möglich, dass mehrere Volumenkörper in dem Ventilgehäuse oder der Aktorausnehmung angeordnet sind, die die gerade beschriebenen Funktionen erfüllen.Also, a geometry of the volume body is arbitrarily scalable due to space constraints, so that at least ensures that the volume is spaced from the movable components of the valve and during operation of the motor vehicle not in contact with them and that there is a controlled change in the volume of the Fluid is flowed through. In addition, it is also possible that a plurality of solids are arranged in the valve housing or Aktorausnehmung that meet the functions just described.

Gemäß einer Ausgestaltung des ersten Aspekts umfasst die Aktorbaugruppe einen Aktor und eine Ventilnadel, die in einem Betriebszustand im Zusammenwirken mit einem Dichtsitz einen Fluidfluss eines Fluids in einer Schließposition der Aktorbaugruppe unterbindet und ansonsten freigibt. Dabei weist der Aktor der Aktorbaugruppe die Aktorausnehmung auf und die mindestens eine hydraulische Ausgleichsöffnung ist im Wesentlichen zwischen dem Aktor und der Ventilnadel ausgebildet.According to one embodiment of the first aspect, the actuator assembly comprises an actuator and a valve needle which, in an operating state in cooperation with a sealing seat, prevents and otherwise releases a fluid flow of a fluid in a closing position of the actuator assembly. In this case, the actuator of the actuator assembly on the Aktorausnehmung and the at least one hydraulic compensation opening is formed substantially between the actuator and the valve needle.

Dies beschreibt eine bevorzugte Möglichkeit der Ausgestaltung und Anordnung der Bauteile der Vorrichtung und realisiert so auf einfache Weise die hydraulische Dämpfung durch den Volumenkörper. Dabei ist der Volumenkörper in der Aktorausnehmung beabstandet zu dem Aktor angeordnet und ragt bei einem Öffnungs- oder Schließprozess in den Bereich der mindestens einen hydraulischen Ausgleichsöffnung, sodass sich zum Beispiel die bewegte Ventilnadel der Aktorbaugruppe dem Volumenkörper nähert oder sich von diesem entfernt. Dies ist unter anderem davon abhängig, ob das Ventil zum Beispiel ein nach außen oder nach innen öffnendes Ventil ist. Der Aktor der Aktorbaugruppe umfasst dabei beispielsweise einen Anker oder kann auch selbst als Anker bezeichnet werden.This describes a preferred possibility of the design and arrangement of the components of the device and thus realized in a simple manner, the hydraulic damping by the solid. In this case, the volume body is arranged in the Aktorausnehmung spaced from the actuator and protrudes in an opening or closing process in the region of the at least one hydraulic compensation opening, so that, for example, the moving valve needle of the actuator assembly approaches the solid or away from it. Among other things, this depends on whether the valve is an outwardly or inwardly opening valve, for example. The actuator of the actuator assembly includes, for example, an anchor or can also be called an anchor itself.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts ist der Volumenkörper im Wesentlichen zylinderförmig ausgebildet.According to a further embodiment of the first aspect of the solid body is formed substantially cylindrical.

Auf diese Weise ist der Volumenkörper rotationssymmetrisch ausgestaltet, was zum Beispiel im Zusammenhang mit einem durchströmenden Fluid während des Betriebs des Kraftfahrzeugs einen homogenen Strömungsverlauf und dadurch eine kontrollierte hydraulische Dämpfung ermöglicht.In this way, the volume body is designed rotationally symmetrical, which allows, for example, in connection with a fluid flowing through during operation of the motor vehicle, a homogeneous flow pattern and thereby a controlled hydraulic damping.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts erstreckt sich der Volumenkörper im Wesentlichen entlang der Mittelachse oder ist zumindest im Wesentlichen parallel zu der Mittlachse angeordnet.According to a further embodiment of the first aspect, the solid body extends substantially along the central axis or is arranged at least substantially parallel to the middle axis.

Auf diese Weise wird ein rotationssymmetrischer Aufbau der Vorrichtung ermöglicht, welcher eine bevorzugte Ausgestaltung des Ventils mit hydraulischer Dämpfung ermöglicht. Beispielsweise sind auch der Aktor, die Ventilnadel und die Aktorausnehmung der Aktorbaugruppe rotationssymmetrisch ausgebildet und axial bezogen auf die Mittelachse angeordnet und realisieren so auf einfache und symmetrische Weise eine kontrollierte hydraulische Dämpfung des bewegten Aktors und der bewegten Ventilnadel, bevor diese zum Beispiel auf das Ventilgehäuse trifft.In this way, a rotationally symmetrical structure of the device is made possible, which allows a preferred embodiment of the valve with hydraulic damping. For example are also the actuator, the valve needle and the Aktorausnehmung the Aktorbaugruppe rotationally symmetrical and arranged axially relative to the central axis and realize so in a simple and symmetrical way a controlled hydraulic damping of the moving actuator and the moving valve needle before it hits, for example, the valve body.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts umfasst die Vorrichtung ein Polstück, das benachbart zu dem Aktor der Aktorbaugruppe angeordnet ist und mittels dessen die Aktorbaugruppe magnetisch öffenbar oder schließbar ist. Der Volumenkörper erstreckt sich dabei im Wesentlichen von dem ersten Ende der Aktorbaugruppe bis in den Bereich der mindestens einen hydraulischen Ausgleichsöffnung.According to a further embodiment of the first aspect, the device comprises a pole piece, which is arranged adjacent to the actuator of the actuator assembly and by means of which the actuator assembly is magnetically openable or closable. The volume body extends substantially from the first end of the actuator assembly into the region of the at least one hydraulic compensation opening.

Auf diese Weise wird zum Beispiel ein magnetisch betätigbares Ventil zur Steuerung des Fluidflusses realisiert, bei dem eine kontrollierte hydraulische Dämpfung des durchströmenden Fluids und der bewegten Bauteile des Ventils durch den angeordneten Volumenkörper erzielt wird. In diesem Zusammenhang trifft zum Beispiel während des Betriebs des Ventils die bewegte Aktorbaugruppe mit dem Aktor auf das benachbarte Polstück und verursacht dadurch einen Impulsübertrag, was folglich zu Vibrationen und Geräuschentwicklung führt. Mittels des Volumenkörpers wird der Aufschlag gedämpft und der Impulsübertrag gemindert, was in der Folge der Entstehung von Vibrationen und der Geräuschentwicklung entgegenwirkt.In this way, for example, a magnetically actuated valve for controlling the fluid flow is realized, in which a controlled hydraulic damping of the flowing fluid and the moving components of the valve is achieved by the arranged volume. In this connection, for example, during operation of the valve, the moving actuator assembly with the actuator encounters the adjacent pole piece causing a momentum transfer, thus resulting in vibration and noise. By means of the volume of the impact is damped and reduced the momentum transfer, which counteracts as a result of the formation of vibration and noise.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts ist der Volumenkörper stoffschlüssig und/oder kraftschlüssig und/oder formschlüssig mit dem Polstück gekoppelt.According to a further embodiment of the first aspect of the solid is cohesively and / or non-positively and / or positively coupled to the pole piece.

Diese Ausgestaltung der Vorrichtung zeigt Möglichkeiten auf, wie der Volumenkörper starr und unbeweglich in dem Ventilgehäuse anordbar ist. Beispielsweise sind der Volumenkörper und das Polstück miteinander verschweißt, verklebt oder verklemmt und so gemeinsam unbeweglich in dem Ventilgehäuse angeordnet, während der Aktor und die Ventilnadel der Aktorbaugruppe relativ zu dem Volumenkörper und dem Polstück axial beweglich in dem Ventilgehäuse angeordnet sind.This embodiment of the device shows ways in which the solid body can be arranged rigidly and immovably in the valve housing. For example, the volume body and the pole piece are welded together, glued or clamped and so together immovably arranged in the valve housing, while the actuator and the valve needle of the actuator assembly are arranged axially movable in the valve housing relative to the volume body and the pole piece.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts weist das Polstück eine Polausnehmung auf, in der der Volumenkörper teilweise angeordnet ist.According to a further embodiment of the first aspect, the pole piece has a Polausnehmung in which the solid is partially arranged.

Auf diese Weise ist zum Beispiel ein Teil des Volumenkörpers in die Polausnehmung des Polstücks eingepresst, wodurch beispielsweise eine kraftschlüssige Verbindung des Volumenkörpers mit dem Polstück erfolgt ist.In this way, for example, a part of the volume body is pressed into the Polausnehmung of the pole piece, whereby, for example, a non-positive connection of the volume body is done with the pole piece.

Gemäß einer weiteren Ausgestaltung des ersten Aspekts ist der Volumenkörper einstückig mit dem Polstück ausgebildet.According to a further embodiment of the first aspect of the solid body is formed integrally with the pole piece.

Gemäß eines zweiten Aspekts der Erfindung umfasst eine Hochdruckpumpe eine Vorrichtung gemäß des ersten Aspekts.According to a second aspect of the invention, a high-pressure pump comprises a device according to the first aspect.

Ausführungsbeispiele der Erfindung sind im Folgenden anhand der schematischen Zeichnungen näher erläutert. Es zeigen:

Figur 1
eine schematische Darstellung einer Hochdruckpumpe,
Figuren 2A-2B
ein Ausführungsbeispiel eines nach außen öffnenden Ventils in geöffneter Position,
Figuren 3A-3B
ein Ausführungsbeispiel eines nach außen öffnenden Ventils in geschlossener Position.
Embodiments of the invention are explained in more detail below with reference to the schematic drawings. Show it:
FIG. 1
a schematic representation of a high-pressure pump,
Figures 2A-2B
an embodiment of an outwardly opening valve in the open position,
Figures 3A-3B
an embodiment of an outwardly opening valve in the closed position.

Elemente gleicher Konstruktion oder Funktion sind figurenübergreifend mit den gleichen Bezugszeichen gekennzeichnet.Elements of the same construction or function are identified across the figures with the same reference numerals.

Figur 1 zeigt schematisch eine Hochdruckpumpe 30, die unter anderem eine Fluidzuleitung 33 aufweist. Die Fluidzuleitung 33 ist hydraulisch mit einem Zylinderraum 31 gekoppelt. Die Hochdruckpumpe 30 weist weiterhin eine Fluidableitung 35 auf. Der Zylinderraum 1 ist hydraulisch zwischen der Fluidzuleitung 33 und der Fluidableitung 35 angeordnet. Die Hochdruckpumpe 30 ist insbesondere eine Hochdruckpumpe für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen von Kraftfahrzeugen. FIG. 1 schematically shows a high-pressure pump 30, which has, inter alia, a fluid supply line 33. The fluid supply line 33 is hydraulically coupled to a cylinder space 31. The high-pressure pump 30 also has a fluid drain 35. The cylinder chamber 1 is arranged hydraulically between the fluid supply line 33 and the fluid discharge line 35. The high-pressure pump 30 is in particular a high-pressure pump for a fuel injection system for internal combustion engines of motor vehicles.

Ein Pumpengehäuse 32 der Hochdruckpumpe 30 umgibt den Zylinderraum 1 und die Fluidzuleitung 33 zu dem Zylinderraum 31, sowie die Fluidableitung 35. Während einer Ansaugphase der Hochdruckpumpe 30 wird Fluid durch die Fluidzuleitung 33 in den Zylinderraum 31 aus einem Niederdruckbereich eingesaugt. Beispielsweise ist die Fluidzuleitung 33 mittels einer Vorförderpumpe (nicht explizit dargestellt) mit einem Fluidtank (nicht explizit dargestellt) hydraulisch gekoppelt. An der Fluidzuleitung 33 ist ein Ventil 1 angeordnet, das einen Einlass des Fluids in den Zylinderraum 31 steuert.A pump housing 32 of the high pressure pump 30 surrounds the cylinder chamber 1 and the fluid supply line 33 to the cylinder chamber 31, and the fluid discharge 35. During a suction phase of the high pressure pump 30, fluid is sucked through the fluid supply line 33 into the cylinder chamber 31 from a low pressure region. For example, the fluid supply line 33 is hydraulically coupled by means of a prefeed pump (not explicitly shown) to a fluid tank (not explicitly shown). At the fluid supply line 33, a valve 1 is arranged, which controls an inlet of the fluid into the cylinder chamber 31.

Daraufhin wird das Fluid in dem Zylinderraum 31 mit einem Druck beaufschlagt, beispielsweise durch eine Kolbenbewegung in dem Zylinderraum. Das mit dem Druck beaufschlagte Fluid wird aus dem Zylinderraum 31 durch ein Auslassventil mittels der Fluidableitung 35 aus der Hochdruckpumpe 30 abgeleitet. Beispielsweise ist die Fluidableitung 35 mit einem Rail eines Common Rail Einspritzsystems gekoppelt. Die Hochdruckpumpe 30 ist zum Beispiel eingerichtet, Drücke von bis zu 2000 bar oder mehr bereitzustellen. Im dargestellten Ausführungsbeispiel ist die Hochdruckpumpe 30 eine Kolbenpumpe, die Hochdruckpumpe kann aber auch eine andere Bauform aufweisen.Subsequently, the fluid in the cylinder chamber 31 is subjected to a pressure, for example by a piston movement in the cylinder chamber. The pressurized fluid is discharged from the cylinder chamber 31 through an outlet valve by means of the fluid discharge 35 from the high-pressure pump 30. For example, the fluid discharge line 35 is coupled to a rail of a common rail injection system. The high pressure pump 30 is configured, for example, pressures of up to 2000 bar or more provide. In the illustrated embodiment, the high-pressure pump 30 is a piston pump, but the high-pressure pump can also have a different design.

Figuren 2A und 2B zeigen in einem Querschnitt einen beispielhaften Aufbau des Ventils 1, das magnetisch betätigbar ist und welches ein Ventilgehäuse 3, eine Mittelachse 17 und eine Aktorbaugruppe 5 umfasst. Die Aktorbaugruppe 5 ist bezogen auf die Mittelachse 17 in dem Ventilgehäuse 3 axial beweglich relativ zu dem Ventilgehäuse 3 angeordnet und weist in diesem Ausführungsbeispiel einen Aktor 7 und eine Ventilnadel 9 auf, die während eines Betriebs des Ventils 1 im Zusammenwirken mit einem Dichtsitz 16 einen Fluidfluss eines Fluids in einer Schließposition der Aktorbaugruppe 5, bestehend aus Aktor 7 und Ventilnadel 9, unterbindet und ansonsten freigibt. Der Aktor 7 der Aktorbaugruppe 5 umfasst beispielsweise einen Anker oder kann auch selbst als Anker bezeichnet werden. FIGS. 2A and 2B show in a cross section an exemplary construction of the valve 1 which is magnetically actuated and which comprises a valve housing 3, a central axis 17 and an actuator assembly 5. The Aktorbaugruppe 5 is relative to the central axis 17 in the valve housing 3 axially movable relative to the valve housing 3 and in this embodiment has an actuator 7 and a valve needle 9, which during operation of the valve 1 in cooperation with a sealing seat 16, a fluid flow a fluid in a closed position of the actuator assembly 5, consisting of actuator 7 and valve needle 9, prevents and otherwise releases. The actuator 7 of the actuator assembly 5 includes, for example, an armature or may itself be referred to as an anchor.

Des Weiteren sind in dem Ventilgehäuse 3 ein Polstück 21 und eine Feder 19 angeordnet, die einen Öffnungs- und Schließprozess des Ventils 1 realisieren. Die Feder 19 übt in diesem Zusammenhang eine Federkraft auf die Aktorbaugruppe 5 aus und drückt dadurch den Aktor 7 der Aktorbaugruppe 5 von dem Polstück 21 weg. Ohne Bestromung des Polstücks 21, d. h. ohne Anlegen einer Spannung an eine magnetische Spule 211, die um das Polstück 21 gewickelt ist, ist das Ventil 1 somit dauerhaft geöffnet. Wird das Polstück 21, das heißt die umwickelnde Spule 211 bestromt, wird ein magnetisches Schließen des Ventils 1 ermöglicht, indem eine durch die Bestromung des Polstücks 21 erzeugte magnetische Kraft gegenüber der Federkraft überwiegt und den Aktor 7 der Aktorbaugruppe 5 in Richtung des Polstücks 21 beschleunigt. In diesem Zusammenhang wird in Bezug auf magnetisch betätigbare Ventile zum Beispiel unterschieden, ob diese stromlos geöffnet oder stromlos geschlossen sind. Das hier beschriebene Ventil 1 ist, wie bereits beschrieben, stromlos geöffnet. In weiteren Ausführungsbeispielen kann das Ventil 1 auch so ausgebildet sein, dass es stromlos geschlossen ist.Furthermore, in the valve housing 3, a pole piece 21 and a spring 19 are arranged, which realize an opening and closing process of the valve 1. In this context, the spring 19 exerts a spring force on the actuator assembly 5 and thereby pushes the actuator 7 of the actuator assembly 5 away from the pole piece 21. Without energizing the pole piece 21, ie without applying a voltage to a magnetic coil 211, which is wound around the pole piece 21, the valve 1 is thus permanently open. If the pole piece 21, that is, the winding coil 211 is energized, a magnetic closing of the valve 1 is made possible by a magnetic force generated by the energization of the pole piece 21 outweighs the spring force and accelerates the actuator 7 of the actuator assembly 5 in the direction of the pole piece 21 , In this context, a distinction is made with respect to magnetically actuated valves, for example, whether they are normally open or normally closed. The valve 1 described here is, as already described, normally open. In further embodiments, the valve 1 may also be designed so that it is normally closed.

Der Aktor 7 der Aktorbaugruppe 5 weist in diesem Ausführungsbeispiel im Bereich eines ersten Endes 6 der Aktorbaugruppe 5 eine Aktorausnehmung 11 auf, die sich in die Aktorbaugruppe 5 erstreckt und in der unter anderem ein Teil der Feder 19 angeordnet ist. Darüber hinaus weist auch das Polstück 21 eine Polausnehmung 23 auf, in die sich die Feder 19 erstreckt. Zwischen dem Aktor 7 und der Ventilnadel 9 sind hydraulische Ausgleichsöffnungen 13 ausgebildet, die während des Betriebs des Ventils 1 den Fluidfluss von einem Außenbereich 12 der Aktorbaugruppe 5 in die Aktorausnehmung 11 ermöglichen.In this exemplary embodiment, the actuator 7 of the actuator assembly 5 has, in the region of a first end 6 of the actuator assembly 5, an actuator recess 11 which extends into the actuator assembly 5 and in which, inter alia, part of the spring 19 is arranged. In addition, the pole piece 21 has a Polausnehmung 23, in which the spring 19 extends. Between the actuator 7 and the valve needle 9 hydraulic compensation openings 13 are formed, which allow the fluid flow from an outer region 12 of the actuator assembly 5 in the Aktorausnehmung 11 during operation of the valve 1.

In der Aktorausnehmung 11 und der Polausnehmung 23 ist ein Volumenkörper 15 angeordnet, der sich bis in einen Bereich 14 der hydraulischen Ausgleichsöffnungen 13 erstreckt. In diesem Ausführungsbeispiel ist der Volumenkörper 15 beispielsweise kraftschlüssig mit dem Polstück 21 verbunden und wurde zum Beispiel im Rahmen eines Herstellungsprozesses in das Polstück 21 eingepresst. Der Volumenkörper 15 ist im Wesentlichen zylinderförmig ausgebildet und weist in der Polausnehmung 23 einen breiteren und in der Aktorausnehmung 11 einen schmaleren zylindrischen Körper in Form eines Stiftes auf. In weiteren Ausführungsbeispielen kann der Volumenkörper 15 andere geometrische Formen aufweisen.In the Aktorausnehmung 11 and the Polausnehmung 23 a volume body 15 is arranged, which extends into a region 14 of the hydraulic compensation openings 13. In this exemplary embodiment, the volume body 15 is, for example, positively connected to the pole piece 21 and, for example, was pressed into the pole piece 21 as part of a production process. The volume body 15 is essentially cylindrical and has a wider cylindrical body in the pole recess 23 and a narrower cylindrical body in the form of a pin in the actuator recess 11. In other embodiments, the solid 15 may have other geometric shapes.

In Figur 2B ist der Bereich 14 der hydraulischen Ausgleichsöffnungen 13 des Ventils 1 im Detail dargestellt. In dieser Ansicht ist ein Teil der Aktorbaugruppe 5 sowie des Aktors 7 und der Ventilnadel 9 vergrößert dargestellt.In FIG. 2B the area 14 of the hydraulic compensation openings 13 of the valve 1 is shown in detail. In this view, a part of the actuator assembly 5 and the actuator 7 and the valve needle 9 is shown enlarged.

In dem Betrieb des Ventils 1 fließt das Fluid, zum Beispiel ein Kraftstoff, in das Ventil 1 und das Ventilgehäuse 3 ein und erreicht den Bereich 14 der hydraulischen Ausgleichsöffnungen 13. Im weiteren Verlauf strömt das Fluid durch die hydraulischen Ausgleichsöffnungen 13 und gelangt so in die Aktorausnehmung 11 des Aktors 7 der Aktorbaugruppe 5. In diesem Zusammenhang umströmt das Fluid den Volumenkörper 15 und die Feder 19, sodass ein Strömungsverlauf des Fluids durch den Volumenkörper 15 beeinflusst wird. Der Volumenkörper 15 verändert ein für das Fluid zugängliches Volumen im Bereich 14 der hydraulischen Ausgleichsöffnungen 13, sodass eine kontrollierte hydraulische Dämpfung des Fluids und der bewegten Bauteile des Ventils 1 erzielt wird.In the operation of the valve 1, the fluid, for example a fuel, flows into the valve 1 and the valve housing 3 and reaches the area 14 of the hydraulic compensation openings 13. In the further course, the fluid flows through the hydraulic compensation openings 13 and thus enters the Aktorausnehmung 11 of the actuator 7 of the actuator assembly 5. In this context, the fluid flows around the volume body 15 and the spring 19, so that a flow pattern of the fluid is influenced by the volume body 15. The volume body 15 changes a volume accessible to the fluid in the region 14 of the hydraulic compensation openings 13, so that a controlled hydraulic damping of the fluid and the moving components of the valve 1 is achieved.

In einer geöffneten Position des Ventils 1 ist zwischen dem Polstück 21 und dem Aktor 7 der Aktorbaugruppe 5 ein Hub 10 vorhanden, der zum Beispiel bei einer Konstruktion des Ventils 1 vorgegeben ausgebildet wird. Außerdem ragt der Volumenkörper 15 in der geöffneten Position des Ventils 1 nicht in den Bereich der hydraulischen Ausgleichsöffnungen 13 hinein und beeinflusst dadurch nicht den Querschnitt und das Volumen der hydraulischen Ausgleichsöffnungen 13 für das durchströmende Fluid. Im Rahmen eines Schließprozesses wird der Hub 10 zwischen dem Polstück 21 und dem Aktor 7 geschlossen, indem das Polstück 21 bestromt wird und die dadurch erzeugte magnetische Kraft der durch die Feder 19 wirkenden Federkraft überwiegt. Dabei wird Fluid aus der Aktorausnehmung 11 durch die hydraulischen Ausgleichsbohrungen 13 gepresst und gelangt so in den Außenbereich 12 der Aktorbaugruppe 5.In an open position of the valve 1, a stroke 10 is present between the pole piece 21 and the actuator 7 of the actuator assembly 5, which is formed for example in a design of the valve 1 predetermined. In addition, in the open position of the valve 1, the volume body 15 does not protrude into the area of the hydraulic compensation openings 13 and thereby does not influence the cross section and the volume of the hydraulic compensation openings 13 for the fluid flowing through. As part of a closing process, the hub 10 between the pole piece 21 and the actuator 7 is closed by the pole piece 21 is energized and outweighs the magnetic force generated thereby acting through the spring 19 spring force. In this case, fluid is pressed out of the actuator recess 11 through the hydraulic compensation bores 13 and thus arrives in the outer region 12 of the actuator assembly 5.

Figur 3A zeigt das Ventil 1 in einem Querschnitt in der geschlossenen Position, in der der Volumenkörper 15 in den Bereich 14 der hydraulischen Ausgleichsöffnungen 13 hineinragt. Im Rahmen des Schließprozesses hat der Volumenkörper 15 den Querschnitt und das Volumen in dem Bereich 14 der hydraulischen Ausgleichsöffnungen 13 verändert und dadurch gezielt ein Ausströmen des Fluids aus der Aktorausnehmung 11 beeinflusst. FIG. 3A shows the valve 1 in a cross section in the closed position in which the volume body 15 projects into the region 14 of the hydraulic compensation openings 13. As part of the closing process, the volume 15 has the Cross-section and the volume in the region 14 of the hydraulic equalization openings 13 changed and thereby specifically influences an outflow of the fluid from the Aktorausnehmung 11.

Auf diese Weise wird eine kontrollierte hydraulische Dämpfung erzielt, die eine Bewegung des Aktors 7 in Richtung des Polstücks 21 bremst und dadurch eine Aufschlagskraft und einen Impulsübertrag auf das Polstücks 21 und/oder das Ventilgehäuse 3 reduziert. Dies wirkt sich dahingehend vorteilhaft aus, dass einer Entstehung von Vibrationen und einer Geräuschentwicklung entgegengewirkt wird.In this way, a controlled hydraulic damping is achieved, which brakes a movement of the actuator 7 in the direction of the pole piece 21 and thereby reduces an impact force and a momentum transfer to the pole piece 21 and / or the valve housing 3. This has the advantage that the formation of vibrations and noise is counteracted.

Das durchströmende Fluid hat aufgrund des Volumenkörpers 15 weniger Volumen beim Ausströmen aus der Aktorausnehmung 11 durch die hydraulischen Ausgleichsöffnungen 13 zur Verfügung, sodass die Bewegung der Aktorbaugruppe 5 durch eine gedrosselte Bewegung des Fluids beeinflusst wird.Due to the volume body 15, the fluid flowing through has less volume when it flows out of the actuator recess 11 through the hydraulic compensation openings 13, so that the movement of the actuator assembly 5 is influenced by a throttled movement of the fluid.

Figur 3B zeigt das in Figur 3A dargestellte Ventil 1 in geschlossener Position mit einer Detailansicht des Bereichs 14 der hydraulischen Ausgleichsöffnungen 13. Der Volumenkörper 15 ragt im Unterschied zu der Position aus Figur 2A und 2B mit einem Ende in den Bereich 14 der hydraulischen Ausgleichsöffnungen 13 rein und verändert dadurch das für das durchströmende Fluid zugängliche Volumen. Diese Volumenänderung wirkt sich entsprechend auch bei einem nachfolgenden Öffnungsprozess des Ventils 1 aus, sodass aufgrund des Volumenkörpers 15 zum Beispiel auch die Bewegung der Ventilnadel 9 beim Öffnen des Ventils 1 aus den beschriebenen Gründen gedämpft wird und die Aufschlagskraft und der Impulsübertrag reduziert werden. FIG. 3B shows that in FIG. 3A illustrated valve 1 in the closed position with a detailed view of the area 14 of the hydraulic compensation openings 13. The volume body 15 projects in contrast to the position FIGS. 2A and 2B with one end into the region 14 of the hydraulic compensation openings 13 purely and thereby changes the volume accessible to the fluid flowing through. This volume change has a corresponding effect on a subsequent opening process of the valve 1, so that due to the volume body 15, for example, the movement of the valve needle 9 is attenuated when opening the valve 1 for the reasons described and the impact force and the momentum transfer are reduced.

Das in den Figuren 2A, 2B, 3A und 3B dargestellte Ventil 1 ermöglicht somit auf einfache Weise durch den starr angeordneten Volumenkörper 15 eine hydraulische Dämpfung der bewegten Bauteile des Ventils 1, wie zum Beispiel den Aktor 7 und die Ventilnadel 9 der Aktorbaugruppe 5 bei einem Öffnungs- und Schließprozess des Ventils 1. Auf diese Weise werden beweglich angeordnete Bauteile des Ventils 1 nicht verändert, sodass zum Beispiel auch eine Masse der Aktorbaugruppe 5 unverändert bleibt. Eine Anordnung des Volumenkörpers 15 zum Beispiel an der Aktorbaugruppe 5 kann unter Umständen auch zu einer Dämpfung einer Bewegung der Aktorbaugruppe 5 führen, führt aber auch aufgrund der Erhöhung der bewegten Masse zu einem erhöhten Impuls, was die Wirkung einer erwünschten hydraulischen Dämpfung wiederum reduziert. Durch die beschriebenen Ausführungsbeispiele wird eine solche Wechselwirkung umgangen.That in the FIGS. 2A, 2B . 3A and 3B illustrated valve 1 thus allows in a simple manner by the rigidly arranged volume body 15, a hydraulic damping of the moving Components of the valve 1, such as the actuator 7 and the valve needle 9 of the actuator assembly 5 in an opening and closing process of the valve 1. In this way, movably arranged components of the valve 1 are not changed, so that, for example, a mass of the actuator assembly. 5 remains unchanged. An arrangement of the volume body 15, for example, on the actuator assembly 5 may also lead to a damping of movement of the actuator assembly 5, but also due to the increase in the mass moved to an increased pulse, which in turn reduces the effect of a desired hydraulic damping. By the described embodiments, such interaction is bypassed.

Außerdem wird die hydraulische Dämpfung mittels des Volumenkörpers 15 im Wesentlichen passiv erzielt, da der Volumenkörper 15 als starres Bauteil des Ventils 1 unbeweglich zum Beispiel relativ zu dem Ventilgehäuse 3 angeordnet ist. Eine aktive hydraulische Dämpfung wird beispielsweise bei einem Magnetventil dadurch erzielt, dass das Polstück 21 bestromt und gegenbestromt wird, um so das Auftreffen des Aktors 7 auf das Polstück 21 oder das Auftreffen der Ventilnadel 9 gegen das Ventilgehäuse 3 abzuschwächen. Dies benötigt zwangsläufig zusätzliche elektrische Leistung und führt zu einem erhöhten Verbrauch des Kraftfahrzeugs.In addition, the hydraulic damping by means of the volume body 15 is achieved substantially passive, since the volume body 15 is arranged as a rigid component of the valve 1 immovable, for example, relative to the valve housing 3. Active hydraulic damping is achieved, for example, in the case of a magnetic valve in that the pole piece 21 is energized and counter-energized so as to attenuate the impact of the actuator 7 on the pole piece 21 or the impact of the valve needle 9 against the valve housing 3. This inevitably requires additional electrical power and leads to increased consumption of the motor vehicle.

Zusätzlich zu der beschriebenen hydraulischen Dämpfung mittels des Volumenkörpers 15 wird ein weiterer nutzbringender Effekt erzielt, dadurch dass die Feder 19 um den Volumenkörper 15 angeordnet ist. Der Volumenkörper 15 hat auf diese Weise auch eine federführende Wirkung, da die Feder 19 an einem Innendurchmesser des Volumenkörpers 15 geführt wird.In addition to the described hydraulic damping by means of the volume body 15, a further beneficial effect is achieved, characterized in that the spring 19 is arranged around the volume body 15. The volume body 15 has in this way also a spring-guiding effect, since the spring 19 is guided on an inner diameter of the volume body 15.

Weiterhin ist eine Anzahl der hydraulischen Ausgleichsöffnungen 13 nicht beschränkt und kann in diesem Zusammenhang beliebig skaliert werden, sodass die mindestens eine oder mehreren hydraulischen Ausgleichsöffnungen 13 die Wandung der Aktorbaugruppe 5 durchdringen und die Aktorausnehmung 11 mit dem Außenbereich 12 der Aktorbaugruppe 5 verbinden. Außerdem ist auch eine Geometrie der mindestens einen hydraulischen Ausgleichsöffnung 13 variabel und kann bauraumbedingt ausgebildet werden. Zum Beispiel ist es vorteilhaft, wenn mehrere hydraulische Ausgleichsöffnungen 13 durch die Wandung der Aktorbaugruppe 5 gebohrt werden.Furthermore, a number of the hydraulic compensation openings 13 is not limited and can be arbitrary in this context are scaled, so that the at least one or more hydraulic compensation openings 13 penetrate the wall of the actuator assembly 5 and connect the Aktorausnehmung 11 with the outer region 12 of the actuator assembly 5. In addition, a geometry of the at least one hydraulic compensation opening 13 is variable and can be formed due to space constraints. For example, it is advantageous if a plurality of hydraulic compensation openings 13 are drilled through the wall of the actuator assembly 5.

Auch eine Geometrie des Volumenkörpers 15 ist bauraumbedingt beliebig skalierbar, sodass zumindest gewährleistet wird, dass der Volumenkörper 15 beabstandet zu beweglichen Bauteilen des Ventils 1, wie dem Aktor 7 und der Ventilnadel 9 der Aktorbaugruppe 5, angeordnet ist und während eines Betriebs des Kraftfahrzeugs nicht mit diesen in Kontakt gerät. Dabei erfolgt durch den Volumenkörper 15 stets eine kontrollierte Veränderung des Volumens in dem Bereich 14 der hydraulischen Ausgleichsöffnungen 13, das während eines Betriebs des Kraftfahrzeugs von dem Fluid durchströmt wird. Darüber hinaus ist es auch möglich, mehrere Volumenkörper 15 in dem Ventilgehäuse 3 oder der Aktorausnehmung 11 anzuordnen, die die beschriebenen Funktionen erfüllen.Also, a geometry of the volume body 15 is arbitrarily scalable due to space constraints, so that at least ensures that the volume body 15 is spaced from movable components of the valve 1, such as the actuator 7 and the valve needle 9 of the actuator assembly 5, and not during operation of the motor vehicle get in contact with them. In this case, the volume body 15 always carries out a controlled change in the volume in the region 14 of the hydraulic compensation openings 13, through which the fluid flows during operation of the motor vehicle. In addition, it is also possible to arrange a plurality of volumetric bodies 15 in the valve housing 3 or the Aktorausnehmung 11, which fulfill the functions described.

Claims (9)

  1. Device for a high-pressure pump for a motor vehicle,
    - which device comprises a valve housing (3), a central axis (17) and an actuator assembly (5) which is arranged substantially along the central axis (17) in the valve housing (3),
    - wherein the actuator assembly (5) has an actuator recess (11) which extends from a first end (6) of the actuator assembly (5) into the actuator assembly (5),
    - wherein the actuator assembly (5) has at least one hydraulic compensation opening (13) which extends through a wall of the actuator assembly (5) from the actuator recess (11) into an exterior region (12), and
    characterized in that the actuator assembly (5) has a volume body (15) which is arranged in the actuator recess (11) so as to be spaced apart from the actuator assembly (5) and which extends into a region (14) of the at least one hydraulic compensation opening (13), wherein the volume body (15) is arranged so as to be immovable relative to the valve housing (3), and the actuator assembly (5) is arranged so as to be movable, axially with respect to the central axis (17), relative to the valve housing (3) and relative to the volume body (15).
  2. Device according to Claim 1,
    - in which the actuator assembly (5) comprises an actuator (7) and a valve needle (9) which, in interaction with a sealing seat (16), prevents a flow of a fluid when the actuator assembly (5) is in a closed position and otherwise permits said flow of fluid, and
    - in which the actuator (7) has the actuator recess (11), and the at least one hydraulic compensation opening (13) is formed substantially between the actuator (7) and the valve needle (9).
  3. Device according to Claim 1 or 2,
    - in which the volume body (15) is of substantially cylindrical form.
  4. Device according to one of Claims 1 to 3,
    - in which the volume body (15) extends substantially along the central axis (17) or is arranged at least substantially parallel to the central axis (17).
  5. Device according to one of Claims 1 to 4,
    - which comprises a pole piece (21) which is arranged adjacent to the actuator (7) of the actuator assembly (5) and by means of which the actuator assembly (5) can be magnetically opened or closed, and
    - in which the volume body (15) extends substantially from the first end (6) of the actuator assembly (5) to the region (14) of the at least one hydraulic compensation opening (13).
  6. Device according to Claim 5,
    - in which the volume body (15) is coupled in cohesive and/or non-positively locking and/or positively locking fashion to the pole piece (21).
  7. Device according to Claim 5 or 6,
    - in which the pole piece (21) has a pole recess (23) in which the volume body (15) is partially arranged.
  8. Device according to Claim 5 or 6,
    - in which the volume body (15) is formed integrally with the pole piece (21).
  9. High-pressure pump for a motor vehicle, which comprises a device according to one of Claims 1 to 8.
EP15733401.2A 2014-08-08 2015-06-24 Device for a high-pressure pump for a motor vehicle Not-in-force EP3036430B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014215774.9A DE102014215774B4 (en) 2014-08-08 2014-08-08 Device for a high-pressure pump for a motor vehicle
PCT/EP2015/064306 WO2016020106A1 (en) 2014-08-08 2015-06-24 Device for a high-pressure pump for a motor vehicle

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EP3036430A1 EP3036430A1 (en) 2016-06-29
EP3036430B1 true EP3036430B1 (en) 2018-02-28

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US (1) US9903357B2 (en)
EP (1) EP3036430B1 (en)
JP (1) JP6084340B2 (en)
KR (1) KR101922315B1 (en)
CN (1) CN105723083B (en)
DE (1) DE102014215774B4 (en)
WO (1) WO2016020106A1 (en)

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DE102014215774B4 (en) 2014-08-08 2016-06-30 Continental Automotive Gmbh Device for a high-pressure pump for a motor vehicle
EP3364015B8 (en) * 2017-02-15 2020-06-03 Vitesco Technologies GmbH Electromagnetic switching valve and high-pressure fuel pump
DE102020202429A1 (en) 2020-02-26 2021-08-26 Hyundai Motor Company Digital inlet valve for a system for direct gasoline injection in a motor vehicle
DE102020206493A1 (en) 2020-05-25 2021-11-25 Hyundai Motor Company Fuel pump for a liquid fuel injection system of a motor vehicle
DE102020206494A1 (en) 2020-05-25 2021-11-25 Hyundai Motor Company Fuel pump for a liquid fuel-water injection system of a motor vehicle

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DE3510222A1 (en) 1985-03-21 1986-09-25 Robert Bosch Gmbh, 7000 Stuttgart SOLENOID VALVE, ESPECIALLY FUEL VOLUME CONTROL VALVE
US4821774A (en) * 1988-04-04 1989-04-18 Chorkey William J Solenoid operated valve with balancing means
DE4137994C2 (en) * 1991-11-19 1999-06-02 Bosch Gmbh Robert Electromagnetically actuated injection valve with a nozzle holder and method for producing a nozzle holder of an injection valve
DE102004028886A1 (en) * 2004-06-15 2006-01-05 Robert Bosch Gmbh Fuel injection system
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DE102010061793A1 (en) * 2009-12-29 2011-06-30 Robert Bosch GmbH, 70469 Electromagnetically actuated switching valve, in particular quantity control valve in particular for controlling the delivery rate of a high-pressure fuel pump
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DE102014215774B4 (en) 2014-08-08 2016-06-30 Continental Automotive Gmbh Device for a high-pressure pump for a motor vehicle

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JP2017501328A (en) 2017-01-12
WO2016020106A1 (en) 2016-02-11
US20170261115A1 (en) 2017-09-14
DE102014215774A1 (en) 2016-02-11
KR101922315B1 (en) 2018-11-26
DE102014215774B4 (en) 2016-06-30
KR20160089493A (en) 2016-07-27
CN105723083A (en) 2016-06-29
US9903357B2 (en) 2018-02-27
EP3036430A1 (en) 2016-06-29
CN105723083B (en) 2018-10-16
JP6084340B2 (en) 2017-02-22

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