EP2938874B1 - Valve arrangement - Google Patents

Valve arrangement Download PDF

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Publication number
EP2938874B1
EP2938874B1 EP14776896.4A EP14776896A EP2938874B1 EP 2938874 B1 EP2938874 B1 EP 2938874B1 EP 14776896 A EP14776896 A EP 14776896A EP 2938874 B1 EP2938874 B1 EP 2938874B1
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EP
European Patent Office
Prior art keywords
valve
housing
valve housing
clamping disk
valve arrangement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14776896.4A
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German (de)
French (fr)
Other versions
EP2938874A1 (en
Inventor
Andreas Mühlbauer
Matthias Bleeck
Burhan Dagdelen
Jörg BERNHARDT
Jürgen Bohmann
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Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
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Publication of EP2938874A1 publication Critical patent/EP2938874A1/en
Application granted granted Critical
Publication of EP2938874B1 publication Critical patent/EP2938874B1/en
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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
    • F02M59/44—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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing
    • 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
    • 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
    • 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
    • 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
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails

Definitions

  • the invention relates to a valve arrangement, in particular a valve arrangement for a high pressure pump for a common rail system.
  • a high-pressure pump in addition to a piston driven by an eccentric, also has a valve arrangement with active or passive valves.
  • the valve assembly is usually integrated by a high degree of integration in sandwich construction directly into the pump, which is done for example by means of pressing and welding operations and accompanying adjustment processes.
  • the valve assembly can be tested in such a production, however, only directly in the pump, so that in case of malfunction of the valve, the entire pump is rejected.
  • DE 10 2010 031 600 A1 discloses a high-pressure pump having a pump element received in a cylinder head and having a suction valve for supplying fuel into the pump element, a closure screw being inserted into the cylinder head which applies an axial force to a suction valve plate of the suction valve applies.
  • the object of the invention is therefore to propose a valve arrangement for a pump, which allows a reliable and also still removable mounting on or in a pump, at the same time installation-related damage Sealing rings prevented and still has a compact construction possible.
  • a valve arrangement for a high pressure pump which has a pump housing with a recess, a valve housing, which is designed to correspond with the recess in the pump housing, so that it can be inserted into the recess, and has a clamping disc.
  • the valve housing has at least one radial projection with a first axial boundary surface and one of these oppositely disposed second axial boundary surface.
  • the clamping disk extends radially over the radial projection of the valve housing and has a third axial boundary surface which rests flush on the second axial boundary surface of the valve housing.
  • the clamping disk has a thread on the circumference, which can be screwed into a thread on the inside of the recess in such a way that the valve housing is clamped by the clamping disk with the first axial boundary surface in the pump housing.
  • valve housing is designed by inserting or insertable by the corresponding configuration in the recess of the pump housing.
  • the interfaces between the valve housing and the pump housing can be configured with conventional sealing rings or the like, which are not rotationally moved due to the lack of screwing the valve housing in the pump housing. The reliability of the sealing effect of the sealing rings is therefore not affected by the nature of the assembly.
  • the radial projection of the valve housing is suitable for carrying out a tensioning of the valve housing with the pump housing via the clamping disk which can be screwed into the pump housing. Due to the high operating pressure in high-pressure pumps of 350 bar or more act on the valve relatively large axial forces that must be absorbed by the attachment of the valve housing. The circumferential arrangement of a thread and the tension of the valve housing with the pump housing leads to a much more favorable absorption of these axial forces, the displacement of the thread radially outward still requires a much smaller dimensioning of the thread and thus allows a compact design of the valve assembly.
  • the recess has a shoulder on which the first axial boundary surface of the valve housing rests. This step can thus provide an annular boundary surface for clamping the valve housing in the pump housing.
  • the shoulder is preferably a stepped transition from a larger inner diameter to a smaller inner diameter. The larger inner diameter could be about the inner diameter of the thread in the recess or fall below this.
  • the recess may have a further shoulder, which leads to a blind hole-like design of the inner portion of the recess.
  • a cylindrical portion of a valve housing can be easily inserted, wherein the valve housing should be easy to insert into the recess.
  • This inner portion of the recess is hereinafter referred to as sealing portion.
  • the sealing portion is designed with a suitable for sealing via a sealing ring fit, wherein the valve housing in a corresponding, cylindrical portion has an annular, circumferentially arranged annular groove in which a sealing ring is arranged.
  • a support ring may be arranged in the annular groove, which prevents extrusion of the sealing ring in a sealing gap formed between the annular groove and the recess.
  • the second axial boundary surface of the valve housing which faces the clamping disk, has a shoulder which extends axially towards the clamping disk. Consequently, the third axial boundary surface on the clamping disc also have a shoulder which corresponds to the shoulder on the second boundary surface of the valve housing.
  • a centering effect can be produced by means of which a particularly precise alignment of the valve housing is produced and / or maintained when the tensioning disk is screwed to the pump housing.
  • the tensioning pulley has a fourth axial limiting surface arranged opposite the third axial limiting surface and provided with a receiving profile for a tool. Since valve components can extend axially over the pump housing through the clamping disk and the clamping disk could continue to submerge almost completely in the pump housing, it is particularly advantageous if a corresponding tool for screwing the clamping disk can be arranged detachably on the clamping disk. This is achieved by such a profile for receiving a tool, which may have completely different shapes. In addition to spaced apart from a rotation axis bores, between which a kind of claw key can be arranged, also regular, continuous profiles, such as a star-shaped recess are conceivable.
  • valve housing and the clamping disc each have a bore whose diameters correspond with each other.
  • An actuator housing of an actuator of a volume control valve is inserted through the two corresponding bores in the valve housing.
  • Coils of a control electromagnet may be arranged around this actuator housing. Another, surrounding the magnet housing could also be bolted to the clamping disc.
  • the invention further relates to a high-pressure pump with such a valve arrangement.
  • the high pressure pump is in this case in particular the high pressure pump of a common rail system.
  • FIG. 1 shows the valve assembly in a sectional view.
  • the Figures 2a) - 2c ) show differently designed clamping disks with recording profiles for receiving a tool.
  • Fig. 1 shows a valve assembly 2 with a valve housing 4, a clamping plate 6 and an actuator 8 in an actuator housing 10.
  • a core component of the valve assembly 2 is a valve stem 12 which is pressed by a spring 14 on a stop 16, wherein the actuator 8 is an axial movement of the valve stem 12 can exert against the spring force.
  • the opening area between the valve tappet 12 and the valve seat 60 is controlled via the actuator 8.
  • the size of the volume flow from a fluid inlet 18 is controlled to an output 20.
  • valve arrangement 2 In order to be able to test and / or replace the individual components of the valve arrangement 2 separately, the valve arrangement 2 according to the invention has a mechanical separation of functions, which leads to the construction shown.
  • the valve housing 4 is designed such that it can be inserted into a recess 22 of a pump housing 24. This means that the valve housing 4 can be pushed into the recess 22 by an axial movement and in this case no rotation, for example for screwing, is necessary.
  • the recess 22 is provided as a blind hole with a flat bottom or with a kegligen reason, with this the output 20 connects.
  • the recess 22 is cylindrical in the region of the outlet 20, as well as the valve housing 4 has a cylindrical portion 26 whose outer diameter corresponds to the inner diameter of the recess 22.
  • the cylindrical portion 26 has a circumferentially arranged annular groove 28 with a support ring which carries a sealing ring 30.
  • the pump housing 24 has a shoulder 34, wherein the inner diameter of the shoulder 34 is smaller than the outer diameter of a projection 36 of the valve housing 4.
  • the valve housing 4 passes when inserted into the recess 22 with a first axial boundary surface 5 in a stop the shoulder 34, so that the geometric positions of inflow channels of the inlet 18 with flow openings 38 of the valve housing 4 correspond.
  • the clamping ring 6 is used for clamping the valve housing 4 with the pump housing 24. This is configured such that on its outside circumference a thread 40 is arranged, which corresponds to a thread 42 of the pump housing 24. The resulting from the high pressure of a common rail system hydraulic force FH is compensated by an applied by means of the clamping ring 6 axial clamping force FS.
  • the valve housing 4 has, on a side facing the clamping ring 6, a second axial limiting surface 44 which corresponds to a third axial limiting surface 46 on a side of the clamping ring 6 facing the valve housing 4.
  • the clamping ring 6 rests during screwing therefore with the third axial boundary surface 46 on the second axial boundary surface.
  • the second axial boundary surface 44 may be bounded by a shoulder 45, which forms an annular plateau facing away from the clamping ring 6.
  • a shoulder 47 of the clamping ring 6 correspond, so that automatically takes place during clamping of the clamping ring 6, a centering of the valve housing 4.
  • the clamping disk 6 is preferably dimensioned such that it is flush in a strained state of the valve housing 4 flush with the pump housing 24 or even slightly immersed in this.
  • valve housing 4 and the clamping disk 6 further each have a central bore 50 and 52, which have the same diameter, so that the actuator housing 10 in the two aligned bores 50 and 52 can be inserted.
  • the remaining components of the actuator 8 can be attached to the clamping disk 6 after assembly of the actuator housing 10.
  • valve assembly can be configured as a separate hydraulic assembly significantly shorter and much more compact. This is achieved by the outsourcing of the thread on an outsourced by the valve housing component having a much larger outer diameter than the cylindrical portion 26. Consequently, a shorter thread is necessary to introduce the same clamping force.
  • valve housing 4 must only be plugged in and a rotation of the valve housing 4 is eliminated, which advantageously exerts on the sealing effect of the sealing ring 30.
  • Fig. 2a - 2c show different receiving profiles 54, 56 and 58 in a clamping disc 6, which are designed to receive a tool. While Fig. 2a shows four radially outwardly extending recesses 54 on the bore 52 is in Fig. 2b proposed to use separate, radially spaced from the bore 52 holes 56. Fig. 2c shows a series of circumferentially arranged on the bore 52, triangular recesses 58 which extend the bore 52 to a tooth profile.
  • Allen recording profiles should be common, however, that a distance to a rotation axis of the clamping plate 6 is maintained and At least two recesses should be present to allow the insertion of the tool outside the central bore 52.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)

Description

Die Erfindung betrifft eine Ventilanordnung, insbesondere eine Ventilanordnung für eine Hochdruckpumpe für ein Common-Rail-System.The invention relates to a valve arrangement, in particular a valve arrangement for a high pressure pump for a common rail system.

Als Common-Rail-Systeme bekannte Einspritzanlagen zum Einspritzen von Kraftstoff in Brennräume einer Brennkraftmaschine, insbesondere eines Dieselmotors, weisen einen druckbeaufschlagten Kraftstoffspeicher, den Common-Rail, auf. Um diesen kontinuierlich mit Kraftstoff zu versorgen, ist eine Hochdruckpumpe erforderlich.As common rail systems known injection systems for injecting fuel into combustion chambers of an internal combustion engine, in particular a diesel engine, have a pressurized fuel storage, the common rail on. To supply this fuel continuously, a high-pressure pump is required.

Eine Hochdruckpumpe weist neben einem über einen Exzenter angetriebenen Kolben auch eine Ventilanordnung mit aktiven oder passiven Ventilen auf. Die Ventilanordnung ist üblicherweise durch einen hohen Integrationsgrad in Sandwich-Bauweise direkt in die Pumpe integriert, was etwa mit Hilfe von Press- und Schweißvorgängen sowie begleitenden Einstellprozessen erfolgt. Die Ventilanordnung kann bei einer derartigen Herstellung allerdings nur direkt in der Pumpe getestet werden, so dass bei Fehlfunktionen des Ventils die gesamte Pumpe Ausschuss wird.A high-pressure pump, in addition to a piston driven by an eccentric, also has a valve arrangement with active or passive valves. The valve assembly is usually integrated by a high degree of integration in sandwich construction directly into the pump, which is done for example by means of pressing and welding operations and accompanying adjustment processes. The valve assembly can be tested in such a production, however, only directly in the pump, so that in case of malfunction of the valve, the entire pump is rejected.

Aus WO 2013/079693 A1 ist bekannt, ein Ventil mit Hilfe eines Zentralgewindes demontierbar an einer Hochdruckpumpe anzubringen. Durch die Anordnung des Zentralgewindes an einem Ventilgehäuse und durch die erforderliche Verwendung von Dichtungsringen an dem Ventilgehäuse erfahren diese eine rotatorisch-translatorische Bewegung während der Montage und können sich hierbei verklemmen oder beschädigt werden.Out WO 2013/079693 A1 It is known to attach a valve by means of a central thread removable on a high-pressure pump. The arrangement of the central thread on a valve housing and the required use of sealing rings on the valve housing, they undergo a rotational-translational movement during assembly and may jam or be damaged here.

DE 10 2010 031 600 A1 offenbart eine Hochddruckpumpe mit einem in einem Zylinderkopf aufgenommenen Pumpenelement, das ein Saugventil zum Zuführen von Kraftstoff in das Pumpenelement aufweist, wobei eine Verschlussschraube in den Zylinderkopf eingesetzt ist, welche eine axiale Kraft auf eine Saugventilplatte des Saugventils aufbringt. DE 10 2010 031 600 A1 discloses a high-pressure pump having a pump element received in a cylinder head and having a suction valve for supplying fuel into the pump element, a closure screw being inserted into the cylinder head which applies an axial force to a suction valve plate of the suction valve applies.

Die Aufgabe der Erfindung liegt folglich darin, eine Ventilanordnung für eine Pumpe vorzuschlagen, die eine möglichst zuverlässige und zudem noch demontierbare Befestigung an oder in einer Pumpe erlaubt, gleichzeitig montagebedingte Schäden von Dichtungsringen verhindert und dennoch einen möglichst kompakten Aufbau aufweist.The object of the invention is therefore to propose a valve arrangement for a pump, which allows a reliable and also still removable mounting on or in a pump, at the same time installation-related damage Sealing rings prevented and still has a compact construction possible.

Die Aufgabe wird durch eine Ventilanordnung mit den Merkmalen des unabhängigen Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen und Ausführungsformen sind den Unteransprüchen und der nachfolgenden Beschreibung zu entnehmen.The object is achieved by a valve arrangement having the features of the independent claim 1. Advantageous developments and embodiments are given in the dependent claims and the following description.

Es wird eine Ventilanordnung für eine Hochdruckpumpe vorgeschlagen, die ein Pumpengehäuse mit einer Vertiefung, ein Ventilgehäuse, welches mit der Vertiefung in dem Pumpengehäuse korrespondierend ausgestaltet ist, so dass es in die Vertiefung einsetzbar ist, und eine Spannscheibe aufweist. Das Ventilgehäuse weist mindestens einen radialen Vorsprung mit einer ersten axialen Begrenzungsfläche und einer dieser gegenüberliegend angeordneten zweiten axialen Begrenzungsfläche auf. Die Spannscheibe erstreckt sich radial über den radialen Vorsprung des Ventilgehäuses und weist eine dritte axiale Begrenzungsfläche auf, die auf der zweiten axialen Begrenzungsfläche des Ventilgehäuses bündig aufliegt. Die Spannscheibe weist umfangsseitig ein Gewinde auf, welches in ein Gewinde an der Innenseite der Vertiefung derart einschraubbar ist, dass das Ventilgehäuse über die Spannscheibe mit der ersten axialen Begrenzungsfläche in dem Pumpengehäuse verspannt wird.It is proposed a valve arrangement for a high pressure pump, which has a pump housing with a recess, a valve housing, which is designed to correspond with the recess in the pump housing, so that it can be inserted into the recess, and has a clamping disc. The valve housing has at least one radial projection with a first axial boundary surface and one of these oppositely disposed second axial boundary surface. The clamping disk extends radially over the radial projection of the valve housing and has a third axial boundary surface which rests flush on the second axial boundary surface of the valve housing. The clamping disk has a thread on the circumference, which can be screwed into a thread on the inside of the recess in such a way that the valve housing is clamped by the clamping disk with the first axial boundary surface in the pump housing.

Das Ventilgehäuse ist durch die korrespondierende Ausgestaltung in die Vertiefung des Pumpengehäuses einsteck- bzw. einschiebbar ausgestaltet. Die Grenzflächen zwischen dem Ventilgehäuse und dem Pumpengehäuse können mit herkömmlichen Dichtungsringen oder dergleichen ausgestaltet werden, die aufgrund der fehlenden Verschraubung des Ventilgehäuses in dem Pumpengehäuse rotatorisch nicht bewegt werden. Die Zuverlässigkeit der Dichtwirkung der Dichtungsringe wird durch die Art der Montage daher nicht beeinflusst.The valve housing is designed by inserting or insertable by the corresponding configuration in the recess of the pump housing. The interfaces between the valve housing and the pump housing can be configured with conventional sealing rings or the like, which are not rotationally moved due to the lack of screwing the valve housing in the pump housing. The reliability of the sealing effect of the sealing rings is therefore not affected by the nature of the assembly.

Der radiale Vorsprung des Ventilgehäuses ist dazu geeignet, über die in das Pumpengehäuse einschraubbare Spannscheibe eine Verspannung des Ventilgehäuses mit dem Pumpengehäuse auszuführen. Aufgrund des hohen Betriebsdruckes in Hochdruckpumpen von 350 bar oder mehr wirken auf das Ventil relativ große axiale Kräfte, die durch die Befestigung des Ventilgehäuses aufgefangen werden müssen. Die umfangsseitige Anordnung eines Gewindes und die Verspannung des Ventilgehäuses mit dem Pumpengehäuse führt zu einer deutlich günstigeren Aufnahme dieser axialen Kräfte, die Verlagerung des Gewindes radial nach außen erfordert weiterhin eine deutlich geringere Dimensionierung des Gewindes und erlaubt damit eine kompakte Gestaltung der Ventilanordnung.The radial projection of the valve housing is suitable for carrying out a tensioning of the valve housing with the pump housing via the clamping disk which can be screwed into the pump housing. Due to the high operating pressure in high-pressure pumps of 350 bar or more act on the valve relatively large axial forces that must be absorbed by the attachment of the valve housing. The circumferential arrangement of a thread and the tension of the valve housing with the pump housing leads to a much more favorable absorption of these axial forces, the displacement of the thread radially outward still requires a much smaller dimensioning of the thread and thus allows a compact design of the valve assembly.

In einer vorteilhaften Ausführungsform weist die Vertiefung einen Absatz auf, auf dem die erste axiale Begrenzungsfläche des Ventilgehäuses aufliegt. Dieser Absatz kann folglich eine ringförmige Begrenzungsfläche zum Verspannen des Ventilgehäuses in dem Pumpengehäuse bereitstellen. Der Absatz ist bevorzugt ein stufenförmiger Übergang von einem größeren Innendurchmesser zu einem kleineren Innendurchmesser. Der größere Innendurchmesser könnte etwa der Innendurchmesser des Gewindes in der Vertiefung sein oder diesen unterschreiten.In an advantageous embodiment, the recess has a shoulder on which the first axial boundary surface of the valve housing rests. This step can thus provide an annular boundary surface for clamping the valve housing in the pump housing. The shoulder is preferably a stepped transition from a larger inner diameter to a smaller inner diameter. The larger inner diameter could be about the inner diameter of the thread in the recess or fall below this.

Zur verbesserten Zentrierung des Ventilgehäuses in dem Pumpengehäuse kann die Vertiefung einen weiteren Absatz aufweisen, der zu einer sacklochartigen Gestaltung des innen liegenden Abschnitts der Vertiefung führt. In diesen Abschnitt kann ein zylinderförmiger Abschnitt eines Ventilgehäuses leicht eingeführt werden, wobei das Ventilgehäuse leicht in die Vertiefung einführbar sein sollte. Dieser innen liegende Abschnitt der Vertiefung wird im Folgenden Dichtabschnitt genannt.For improved centering of the valve housing in the pump housing, the recess may have a further shoulder, which leads to a blind hole-like design of the inner portion of the recess. In this section, a cylindrical portion of a valve housing can be easily inserted, wherein the valve housing should be easy to insert into the recess. This inner portion of the recess is hereinafter referred to as sealing portion.

Besonders bevorzugt ist der Dichtabschnitt mit einer für eine Abdichtung über einen Dichtungsring geeigneten Passung ausgeführt, wobei das Ventilgehäuse in einem korrespondierenden, zylindrischen Abschnitt eine ringförmige, umfangsseitig angeordnete Ringnut besitzt, in der ein Dichtungsring angeordnet ist. Beim Einschieben des Ventilgehäuses in den Dichtabschnitt erfolgt eine Verquetschung des Dichtungsrings und folglich eine Abdichtung zwischen dem Dichtabschnitt und dem Ventilgehäuse. Wie vorangehend ausgeführt, wird durch das Einschieben eine kontinuierliche Rotation des Dichtungsrings bei der Montage vermieden. Damit kann nahezu ausgeschlossen werden, dass die Dichtwirkung montagebedingt beeinträchtigt wird.Particularly preferably, the sealing portion is designed with a suitable for sealing via a sealing ring fit, wherein the valve housing in a corresponding, cylindrical portion has an annular, circumferentially arranged annular groove in which a sealing ring is arranged. When inserting the valve housing into the sealing section, there is a squeezing of the sealing ring and consequently a seal between the sealing section and the valve housing. As stated above, the insertion is a continuous rotation of the sealing ring during assembly avoided. Thus, it can almost be ruled out that the sealing effect is impaired due to assembly.

Weiter vorteilhaft kann ein Stützring in der Ringnut angeordnet sein, der ein Extrudieren des Dichtungsrings in einen zwischen der Ringnut und der Vertiefung gebildeten Dichtspalt verhindert.Further advantageously, a support ring may be arranged in the annular groove, which prevents extrusion of the sealing ring in a sealing gap formed between the annular groove and the recess.

In einer vorteilhaften Ausführungsform weist die zweite axiale Begrenzungsfläche des Ventilgehäuses, die zu der Spannscheibe gewandt ist, einen sich axial zur Spannscheibe hin erstreckenden Absatz auf. Folglich kann die dritte axiale Begrenzungsfläche an der Spannscheibe ebenfalls einen Absatz aufweisen, der mit dem Absatz an der zweiten Begrenzungsfläche des Ventilgehäuses korrespondiert. Damit kann zusätzlich eine Zentrierwirkung hergestellt werden, durch die beim Verschrauben der Spannscheibe mit dem Pumpengehäuse eine besonders präzise Ausrichtung des Ventilgehäuses hergestellt und/oder aufrechterhalten wird.In an advantageous embodiment, the second axial boundary surface of the valve housing, which faces the clamping disk, has a shoulder which extends axially towards the clamping disk. Consequently, the third axial boundary surface on the clamping disc also have a shoulder which corresponds to the shoulder on the second boundary surface of the valve housing. In addition, a centering effect can be produced by means of which a particularly precise alignment of the valve housing is produced and / or maintained when the tensioning disk is screwed to the pump housing.

Als weitere Ausführungsform wäre eine plane Auflage der Begrenzungsflächen denkbar, die damit besonders einfach zu fertigen sind.As a further embodiment, a planar support of the boundary surfaces would be conceivable, which are therefore particularly easy to manufacture.

In einer besonders bevorzugten Ausführungsform weist die Spannscheibe eine der dritten axialen Begrenzungsfläche gegenüberliegend angeordnete vierte axiale Begrenzungsfläche, die mit einem Aufnahmeprofil für ein Werkzeug ausgestattet ist, auf. Da sich Ventilkomponenten durch die Spannscheibe axial über das Pumpengehäuse erstrecken können und die Spannscheibe weiterhin nahezu vollständig in das Pumpengehäuse eintauchen könnte, ist es besonders vorteilhaft, wenn ein entsprechendes Werkzeug zum Verschrauben der Spannscheibe lösbar an der Spannscheibe angeordnet werden kann. Dies wird durch ein solches Profil zur Aufnahme eines Werkzeugs erreicht, welches völlig unterschiedliche Formen aufweisen kann. Neben von einer Drehachse beabstandeten Bohrungen, zwischen die eine Art Klauenschlüssel angeordnet werden kann, sind auch regelmäßige, durchgehende Profile, wie etwa eine sternförmige Ausnehmung denkbar.In a particularly preferred embodiment, the tensioning pulley has a fourth axial limiting surface arranged opposite the third axial limiting surface and provided with a receiving profile for a tool. Since valve components can extend axially over the pump housing through the clamping disk and the clamping disk could continue to submerge almost completely in the pump housing, it is particularly advantageous if a corresponding tool for screwing the clamping disk can be arranged detachably on the clamping disk. This is achieved by such a profile for receiving a tool, which may have completely different shapes. In addition to spaced apart from a rotation axis bores, between which a kind of claw key can be arranged, also regular, continuous profiles, such as a star-shaped recess are conceivable.

Das Ventilgehäuse und die Spannscheibe weisen jeweils eine Bohrung auf, deren Durchmesser miteinander korrespondieren. Ein Aktuatorgehäuse eines Aktuators eines Volumensteuerventils ist durch die beiden korrespondierenden Bohrungen in das Ventilgehäuse eingesteckt. Um dieses Aktuatorgehäuse herum können Spulen eines Steuer-Elektromagneten angeordnet sein. Ein weiteres, den Magneten umgebendes Gehäuse könnte ferner mit der Spannscheibe verschraubt werden.The valve housing and the clamping disc each have a bore whose diameters correspond with each other. An actuator housing of an actuator of a volume control valve is inserted through the two corresponding bores in the valve housing. Coils of a control electromagnet may be arranged around this actuator housing. Another, surrounding the magnet housing could also be bolted to the clamping disc.

Die Erfindung betrifft ferner eine Hochdruckpumpe mit einer derartigen Ventilanordnung. Die Hochdruckpumpe ist hierbei insbesondere die Hochdruckpumpe eines Common-Rail-Systems.The invention further relates to a high-pressure pump with such a valve arrangement. The high pressure pump is in this case in particular the high pressure pump of a common rail system.

Die beschriebenen Ausgestaltungen und Weiterbildungen lassen sich beliebig miteinander kombinieren.The described embodiments and developments can be combined with each other as desired.

Weitere mögliche Ausgestaltungen, Weiterbildungen und Implementierungen der Erfindung umfassen auch nicht explizit genannte Kombinationen von zuvor oder im Folgenden bezüglich der Ausführungsbeispiele beschriebenen Merkmale der Erfindung.Further possible refinements, developments and implementations of the invention also include combinations, not explicitly mentioned, of features of the invention described above or below with regard to the exemplary embodiments.

Die beiliegenden Zeichnungen sollen ein weiteres Verständnis der Ausführungsformen der Erfindung vermitteln. Sie veranschaulichen Ausführungsformen und dienen im Zusammenhang mit der Beschreibung der Erklärung von Konzepten der Erfindung.The accompanying drawings are intended to provide further understanding of the embodiments of the invention. They illustrate embodiments and, together with the description, serve to explain concepts of the invention.

Andere Ausführungsformen und viele der genannten Vorteile ergeben sich im Hinblick auf die Zeichnungen. Die dargestellten Elemente der Zeichnungen sind nicht notwendigerweise maßstabsgetreu zueinander gezeigt.Other embodiments and many of the stated advantages will become apparent with reference to the drawings. The illustrated elements of the drawings are not necessarily shown to scale to each other.

Figur 1 zeigt die Ventilanordnung in einer Schnittdarstellung. FIG. 1 shows the valve assembly in a sectional view.

Die Figuren 2a) - 2c) zeigen unterschiedlich ausgeführte Spannscheiben mit Aufnahmeprofilen zum Aufnehmen eines Werkzeugs.The Figures 2a) - 2c ) show differently designed clamping disks with recording profiles for receiving a tool.

In den Figuren der Zeichnungen bezeichnen gleiche Bezugszeichen gleiche oder funktionsgleiche Elemente, Bauteile, Komponenten oder Verfahrensschritte, soweit nichts Gegenteiliges angegeben ist.In the figures of the drawings, like reference characters designate like or functionally identical elements, components, components or method steps, unless indicated otherwise.

Fig. 1 zeigt eine Ventilanordnung 2 mit einem Ventilgehäuse 4, einer Spannscheibe 6 und einem Aktuator 8 in einem Aktuatorgehäuse 10. Eine Kernkomponente der Ventilanordnung 2 ist ein Ventilstößel 12, der über eine Feder 14 auf einen Anschlag 16 gepresst wird, wobei der Aktuator 8 eine axiale Bewegung des Ventilstößels 12 gegen die Federkraft ausüben kann. In Abhängigkeit eines elektrischen Steuerstroms wird über den Aktuator 8 die Öffnungsfläche zwischen dem Ventilstößel 12 und dem Ventilsitz 60 gesteuert. Damit wird die Größe des Volumenstroms aus einem Fluideingang 18 zu einem Ausgang 20 gesteuert. Fig. 1 shows a valve assembly 2 with a valve housing 4, a clamping plate 6 and an actuator 8 in an actuator housing 10. A core component of the valve assembly 2 is a valve stem 12 which is pressed by a spring 14 on a stop 16, wherein the actuator 8 is an axial movement of the valve stem 12 can exert against the spring force. In response to an electrical control current, the opening area between the valve tappet 12 and the valve seat 60 is controlled via the actuator 8. Thus, the size of the volume flow from a fluid inlet 18 is controlled to an output 20.

Um die einzelnen Komponenten der Ventilanordnung 2 separat testen und/oder austauschen zu können, weist die erfindungsgemäße Ventilanordnung 2 eine mechanische Trennung von Funktionen auf, die zu dem gezeigten Aufbau führt. Das Ventilgehäuse 4 ist derart ausgestaltet, dass es in eine Vertiefung 22 eines Pumpengehäuses 24 einsteckbar ist. Dies bedeutet, dass das Ventilgehäuse 4 durch eine axiale Bewegung in die Vertiefung 22 einschiebbar ist und hierbei keine Rotation, beispielsweise zum Schrauben, notwendig ist. Die Vertiefung 22 ist wie ein Sackloch mit ebenem Grund oder mit einem kegligen Grund versehen, wobei sich hieran der Ausgang 20 anschließt.In order to be able to test and / or replace the individual components of the valve arrangement 2 separately, the valve arrangement 2 according to the invention has a mechanical separation of functions, which leads to the construction shown. The valve housing 4 is designed such that it can be inserted into a recess 22 of a pump housing 24. This means that the valve housing 4 can be pushed into the recess 22 by an axial movement and in this case no rotation, for example for screwing, is necessary. The recess 22 is provided as a blind hole with a flat bottom or with a kegligen reason, with this the output 20 connects.

Die Vertiefung 22 ist im Bereich des Ausgangs 20 zylindrisch ausgeführt, ebenso weist das Ventilgehäuse 4 einen zylindrischen Abschnitt 26 auf, dessen Außendurchmesser dem Innendurchmesser der Vertiefung 22 entspricht. Der zylindrische Abschnitt 26 weist eine umfangsseitig angeordnete Ringnut 28 mit einem Stützring auf, die einen Dichtungsring 30 trägt. Durch das Einschieben des Ventilgehäuses 4 in die Vertiefung 22 wird der Dichtungsring 30 leicht komprimiert und dadurch bündig sowohl an den Stützring in der Ringnut 28 als auch an die korrespondierende Dichtfläche 32 des Pumpengehäuses 24 gepresst. Damit entsteht eine gewünschte Dichtwirkung.The recess 22 is cylindrical in the region of the outlet 20, as well as the valve housing 4 has a cylindrical portion 26 whose outer diameter corresponds to the inner diameter of the recess 22. The cylindrical portion 26 has a circumferentially arranged annular groove 28 with a support ring which carries a sealing ring 30. By inserting the valve housing 4 in the recess 22 of the sealing ring 30 is slightly compressed and thereby flush both to the support ring in the annular groove 28 and to the corresponding sealing surface 32 of the pump housing 24 pressed. This creates a desired sealing effect.

Das Pumpengehäuse 24 weist einen Absatz 34 auf, wobei der innere Durchmesser des Absatzes 34 kleiner ist als der äußere Durchmesser eines Vorsprungs 36 des Ventilgehäuses 4. Dadurch gelangt das Ventilgehäuse 4 beim Einschieben in die Vertiefung 22 mit einer ersten axialen Begrenzungsfläche 5 in einen Anschlag mit dem Absatz 34, so dass die geometrischen Positionen von Zuströmkanälen von dem Eingang 18 mit Durchströmöffnungen 38 des Ventilgehäuses 4 korrespondieren.The pump housing 24 has a shoulder 34, wherein the inner diameter of the shoulder 34 is smaller than the outer diameter of a projection 36 of the valve housing 4. As a result, the valve housing 4 passes when inserted into the recess 22 with a first axial boundary surface 5 in a stop the shoulder 34, so that the geometric positions of inflow channels of the inlet 18 with flow openings 38 of the valve housing 4 correspond.

Zum Verspannen des Ventilgehäuses 4 mit dem Pumpengehäuse 24 wird der Spannring 6 eingesetzt. Dieser ist derart ausgestaltet, dass an seiner Außenseite umfangsseitig ein Gewinde 40 angeordnet ist, welches mit einem Gewinde 42 des Pumpengehäuses 24 korrespondiert. Die durch den hohen Druck eines Common-Rail-Systems entstehende hydraulische Kraft FH wird durch eine mit Hilfe des Spannrings 6 aufgebrachte axiale Spannkraft FS kompensiert.For clamping the valve housing 4 with the pump housing 24, the clamping ring 6 is used. This is configured such that on its outside circumference a thread 40 is arranged, which corresponds to a thread 42 of the pump housing 24. The resulting from the high pressure of a common rail system hydraulic force FH is compensated by an applied by means of the clamping ring 6 axial clamping force FS.

Das Ventilgehäuse 4 weist auf einer zu dem Spannring 6 gewandten Seite eine zweite axiale Begrenzungsfläche 44 auf, die mit einer dritten axialen Begrenzungsfläche 46 auf einer zu dem Ventilgehäuse 4 gewandten Seite des Spannrings 6 korrespondiert. Der Spannring 6 legt sich beim Verschrauben daher mit der dritten axialen Begrenzungsfläche 46 auf die zweite axiale Begrenzungsfläche auf.The valve housing 4 has, on a side facing the clamping ring 6, a second axial limiting surface 44 which corresponds to a third axial limiting surface 46 on a side of the clamping ring 6 facing the valve housing 4. The clamping ring 6 rests during screwing therefore with the third axial boundary surface 46 on the second axial boundary surface.

Die zweite axiale Begrenzungsfläche 44 kann durch einen Absatz 45 begrenzt sein, der ein dem Spannring 6 abgewandtes, ringförmiges Plateau bildet. Hiermit kann ein Absatz 47 des Spannrings 6 korrespondieren, so dass beim Verspannen des Spannrings 6 automatisch eine Zentrierung des Ventilgehäuses 4 erfolgt.The second axial boundary surface 44 may be bounded by a shoulder 45, which forms an annular plateau facing away from the clamping ring 6. Hereby, a shoulder 47 of the clamping ring 6 correspond, so that automatically takes place during clamping of the clamping ring 6, a centering of the valve housing 4.

An einer der dritten Begrenzungsfläche 46 gegenüberliegend angeordneten vierten Begrenzungsfläche 48 sind Werkzeugaufnahmeprofile (hier nicht gezeigt) vorhanden, die ein Aufbringen eines Anzugsmoments auf die Spannscheibe 6 erlauben. Die Spannscheibe 6 ist bevorzugt derart dimensioniert, dass sie in einem verspannten Zustand des Ventilgehäuses 4 bündig mit dem Pumpengehäuse 24 abschließt oder sogar leicht in dieses eintaucht.On one of the third boundary surface 46 opposite arranged fourth boundary surface 48 tool receiving profiles (not shown here) are present, the application allow a tightening torque on the clamping plate 6. The clamping disk 6 is preferably dimensioned such that it is flush in a strained state of the valve housing 4 flush with the pump housing 24 or even slightly immersed in this.

Das Ventilgehäuse 4 und die Spannscheibe 6 weisen weiterhin jeweils eine zentrale Bohrung 50 bzw. 52 auf, die den gleichen Durchmesser besitzen, so dass das Aktuatorgehäuse 10 in die beiden miteinander fluchtenden Bohrungen 50 und 52 einsteckbar ist. Die übrigen Bauteile des Aktuators 8 können nach Montage des Aktuatorgehäuses 10 an der Spannscheibe 6 befestigt werden.The valve housing 4 and the clamping disk 6 further each have a central bore 50 and 52, which have the same diameter, so that the actuator housing 10 in the two aligned bores 50 and 52 can be inserted. The remaining components of the actuator 8 can be attached to the clamping disk 6 after assembly of the actuator housing 10.

Durch die Funktionstrennung der Dichtung über den Dichtungsring 30 und die Verspannung des Ventilgehäuses 4 über die Spannscheibe 6 kann die Ventilanordnung als eigenständige hydraulische Baugruppe deutlich kürzer und wesentlich kompakter ausgestaltet werden. Dies wird durch die Auslagerung des Gewindes an einem vom Ventilgehäuse ausgelagerten Bauteil erreicht, das einen deutlich größeren Außendurchmesser als der zylindrische Abschnitt 26 besitzt. Folglich ist zum Einbringen der gleichen Spannkraft ein kürzeres Gewinde notwendig. Zudem muss das Ventilgehäuse 4 nur eingesteckt werden und eine Rotation des Ventilgehäuses 4 entfällt, was sich vorteilhaft auf die Dichtwirkung des Dichtrings 30 ausübt.Due to the separation of functions of the seal on the sealing ring 30 and the tension of the valve housing 4 via the clamping disk 6, the valve assembly can be configured as a separate hydraulic assembly significantly shorter and much more compact. This is achieved by the outsourcing of the thread on an outsourced by the valve housing component having a much larger outer diameter than the cylindrical portion 26. Consequently, a shorter thread is necessary to introduce the same clamping force. In addition, the valve housing 4 must only be plugged in and a rotation of the valve housing 4 is eliminated, which advantageously exerts on the sealing effect of the sealing ring 30.

Die Fig. 2a - 2c zeigen unterschiedliche Aufnahmeprofile 54, 56 und 58 in einer Spannscheibe 6, die zum Aufnehmen eines Werkzeugs ausgestaltet sind. Während Fig. 2a vier sich radial nach außen erstreckende Ausnehmungen 54 an der Bohrung 52 zeigt, wird in Fig. 2b vorgeschlagen, separate, radial von der Bohrung 52 beabstandete Bohrungen 56 einzusetzen. Fig. 2c zeigt eine Reihe von umfangsseitig an der Bohrung 52 angeordneter, dreieckiger Ausnehmungen 58, die die Bohrung 52 zu einem Zahnprofil erweitern. Selbstverständlich sind auch andere Aufnahmeprofile denkbar, ohne den Kern der Erfindung zu verlassen. Allen Aufnahmeprofilen sollte jedoch gemein sein, dass ein Abstand zu einer Rotationsachse der Spannscheibe 6 eingehalten wird und mindestens zwei Ausnehmungen vorhanden sein sollten, um das Einführen des Werkzeugs außerhalb der zentralen Bohrung 52 zu erlauben.The Fig. 2a - 2c show different receiving profiles 54, 56 and 58 in a clamping disc 6, which are designed to receive a tool. While Fig. 2a shows four radially outwardly extending recesses 54 on the bore 52 is in Fig. 2b proposed to use separate, radially spaced from the bore 52 holes 56. Fig. 2c shows a series of circumferentially arranged on the bore 52, triangular recesses 58 which extend the bore 52 to a tooth profile. Of course, other recording profiles are conceivable without departing from the gist of the invention. Allen recording profiles should be common, however, that a distance to a rotation axis of the clamping plate 6 is maintained and At least two recesses should be present to allow the insertion of the tool outside the central bore 52.

Claims (8)

  1. Valve arrangement (2) for a high pressure pump, having
    - a pump housing (24) with a depression (22),
    - a valve housing (4) which is configured so as to correspond with the depression (22) in the pump housing (24), with the result that it can be inserted into the depression (22), and
    - a clamping disk (6),
    the valve housing (4) having at least one radial projection (36) with a first axial bounding face (5) and a second axial bounding face (44) which is arranged so as to lie opposite the former,
    the clamping disk (6) extending radially over the radial projection (36) of the valve housing (4) and having a third axial bounding face (46) which rests flush on the second axial bounding face (44) of the valve housing (4), and
    the clamping disk (6) having a thread (40) on the circumferential side, which thread (40) can be screwed into a thread (42) on the inner side of the depression (22) in such a way that the valve housing (4) is braced in the pump housing via the clamping disk (6), characterized in that the valve housing (4) and the clamping disk (6) have in each case one bore (50, 52), the bores (50, 52) merging into one another and the diameters corresponding with one another, and in that the valve arrangement (2) also has an actuator (8) and an actuator housing (10) of the valve actuator (8) is plugged into the two bores (50, 52).
  2. Valve arrangement (2) according to Claim 1, the depression (22) having a shoulder, on which the first axial bounding face (5) of the valve housing (4) rests.
  3. Valve arrangement (2) according to Claim 1 or 2, the depression (22) in the pump housing (24) having a further shoulder (35) for receiving a cylindrical section (26) of the valve housing (4).
  4. Valve arrangement (2) according to one of the preceding claims, the valve housing (4) having an annular ring groove (28) which is arranged on the circumferential side in a cylindrical section (26) and in which a sealing ring (30) is arranged.
  5. Valve arrangement (2) according to Claim 4, a supporting ring being arranged, furthermore, in the ring groove (28).
  6. Valve arrangement (2) according to one of the preceding claims, that second axial bounding face (44) of the valve housing (4) which faces the clamping disk (6) having a shoulder (45) which extends axially toward the clamping disk (6) and corresponds with a shoulder (47) on the third axial bounding face (46) on the clamping disk (6), with the result that the valve housing (4) is centered on the clamping disk (6).
  7. Valve arrangement (2) according to one of the preceding claims, the clamping disk (6) having a fourth axial bounding face (48) which is arranged so as to lie opposite the third axial bounding face (46) and which is equipped with a receiving profile (54, 56, 58) for a tool.
  8. High pressure pump for a common rail system having a valve arrangement (2) according to one of Claims 1 to 7.
EP14776896.4A 2013-10-15 2014-09-29 Valve arrangement Active EP2938874B1 (en)

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PCT/EP2014/070833 WO2015055410A1 (en) 2013-10-15 2014-09-29 Valve arrangement

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220768A1 (en) 2013-10-15 2015-04-16 Continental Automotive Gmbh valve assembly
ITUB20156824A1 (en) * 2015-12-09 2017-06-09 Magneti Marelli Spa LIGHTENED FUEL PUMP FOR A DIRECT INJECTION SYSTEM AND RELATIVE ASSEMBLY METHOD
EP3346123B1 (en) * 2017-01-10 2019-07-10 Continental Automotive GmbH Electromagnetic switching valve and high-pressure fuel pump for a fuel injection system of a combustion engine
JP6747482B2 (en) * 2017-09-29 2020-08-26 株式会社デンソー High pressure pump
US11661913B2 (en) * 2021-05-17 2023-05-30 Delphi Technologies Ip Limited Fuel pump with inlet valve assembly

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1037822A (en) 1997-03-27 1998-02-13 Zexel Corp Pressure control valve
DE19729791A1 (en) 1997-07-11 1999-01-14 Bosch Gmbh Robert Radial piston pump for high-pressure fuel supply
JP3851056B2 (en) * 2000-04-18 2006-11-29 トヨタ自動車株式会社 High pressure pump
GB0108216D0 (en) * 2001-04-02 2001-05-23 Delphi Tech Inc Fuel Injector
US6648610B2 (en) 2001-04-02 2003-11-18 Delphi Technologies, Inc. Fuel injection system with structurally biased relief valve
JP2004183552A (en) * 2002-12-03 2004-07-02 Denso Corp Fuel high pressure supply pump
JP2005248847A (en) 2004-03-04 2005-09-15 Bosch Automotive Systems Corp Sealing structure for fuel passage and fuel injection valve equipped with the sealing structure
JP4569825B2 (en) * 2005-04-26 2010-10-27 株式会社デンソー High pressure fuel pump
DE602007001130D1 (en) * 2007-03-05 2009-06-25 Magneti Marelli Spa Solenoid valve for fuel metering in an internal combustion engine
US7509948B1 (en) * 2007-10-01 2009-03-31 Caterpillar Inc. Variable displacement pump with an anti-stiction device
DE102009002530A1 (en) 2009-04-21 2010-10-28 Robert Bosch Gmbh High-pressure pump for use in fuel injection system of internal combustion engine, has valve support prestressed against pump cylinder head by clamping element, and sealing device provided between support and head to seal pressure chamber
DE102009029582A1 (en) 2009-09-18 2011-03-24 Robert Bosch Gmbh High pressure pump for delivering fuel into combustion chamber of internal combustion engine, is provided with pump element, where fuel in intake stroke of pump piston is drawn from low pressure area over suction valve
DE102010031600A1 (en) * 2010-07-21 2012-01-26 Robert Bosch Gmbh High pressure pump i.e. radial piston pump, for fuel injector of combustion engine in motor car, has plug comprising sealing collar located underneath screw thread, where filter element designed as wire is arranged in screw thread
DE102011087664B4 (en) 2011-12-02 2014-03-20 Continental Automotive Gmbh valve assembly
DE102011089857A1 (en) * 2011-12-23 2013-06-27 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump for a fuel injection device
DE102013220768A1 (en) 2013-10-15 2015-04-16 Continental Automotive Gmbh valve assembly

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CN105074193A (en) 2015-11-18
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JP5976239B2 (en) 2016-08-23
DE102013220768A1 (en) 2015-04-16
US9719472B2 (en) 2017-08-01
KR20150110769A (en) 2015-10-02
CN105074193B (en) 2019-02-22
KR101679582B1 (en) 2016-11-25
EP2938874A1 (en) 2015-11-04
US20160215744A1 (en) 2016-07-28

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