EP2745002B1 - Valve for dosing a flowing medium - Google Patents

Valve for dosing a flowing medium Download PDF

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Publication number
EP2745002B1
EP2745002B1 EP12729163.1A EP12729163A EP2745002B1 EP 2745002 B1 EP2745002 B1 EP 2745002B1 EP 12729163 A EP12729163 A EP 12729163A EP 2745002 B1 EP2745002 B1 EP 2745002B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve body
valve housing
clamping ring
seal
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
EP12729163.1A
Other languages
German (de)
French (fr)
Other versions
EP2745002A1 (en
Inventor
Dietmar Schmieder
Thomas Sebastian
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2745002A1 publication Critical patent/EP2745002A1/en
Application granted granted Critical
Publication of EP2745002B1 publication Critical patent/EP2745002B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • 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
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9038—Coatings

Definitions

  • the invention is based on a valve for metering a flowing, e.g. gaseous or liquid medium, in particular fuel injection valve for internal combustion engines, according to the preamble of claim 1.
  • a known fuel injection valve ( DE 10 2007 028 490A1 ) has a hollow cylindrical housing with an inlet-side and a discharge-side end. The inflow-side end is closed by a cap carrying an inlet nozzle, and a hollow-cylindrical valve or nozzle body is inserted into the ejection-side end, which protrudes partially out of the housing. At the housing-distal end of the valve body, a spray-discharge opening and a valve seat enclosing the spray-discharge opening are formed.
  • valve housing encloses the valve body, and the existing between valve housing and valve body annular joint is liquid-tight sealed by a valve housing and valve body interconnecting weld, so that in the valve housing under system pressure of eg 200 bar standing fuel can not escape at the joint.
  • the fuel injection valve has a valve housing having an inlet for the medium and a valve body having an orifice for the medium, wherein a joint is present between the valve housing and the valve body and the joint is sealed by a seal.
  • the seal has a joint covering the clamping nut, which is screwed onto the two components valve housing and valve body, each having an external thread with its internal thread. In this way, valve body and valve body are firmly connected and sit tightly screwed together in the joint area.
  • the clamping nut serves to clamp the valve housing and valve body by means of a screw connection.
  • the fuel injection valve is a diesel injector with which, as is known, diesel fuel is injected at pressures well above 1000 bar directly into the combustion chamber of diesel engines, which is why bolted connections are used in this type of injector for reasons of strength.
  • a fuel injection valve for internal combustion engines which is equipped with a valve housing having a feed for the medium to be injected, with a valve body having an orifice for the medium, with a joint present between the valve housing and the valve body and with a seal sealing the joint.
  • the seal has a joint covering the clamping sleeve, which engages by a joining operation by means of a drawing ring frictionally engages in a recess of the valve housing with a bead.
  • the valve according to the invention with the features of claim 1 has the advantage that a secure and rissunan administrate sealing of the joint between the valve housing and the valve body is made by the interference fit on the valve body and valve body the joint overlapping clamping ring in comparison to a weld.
  • the interference fit of the clamping ring is preferably produced by shrinking.
  • valve body and valve body shrinks when cooled and pulls the valve body and the valve housing axially together, whereby between valve body and valve body traction and a radial and axial sealing of the joint is brought about.
  • the interference fit can also be produced by mechanically pressing on the clamping ring pushed onto the end sections of the valve housing and valve body in excess.
  • the material of valve housing and valve body can - unlike a seal by a weld - are freely chosen, since the compulsion to use a very good weldable material to achieve a mechanically stable, pressure and tear resistant weld is eliminated.
  • valve body and valve body can be made of inexpensive material and the production costs are reduced.
  • a reliable and good positional positioning of the two parts is achieved.
  • a reliable sealing of the joint can be ensured even with a large outer diameter of the valve body despite high pressures in the valve housing.
  • a large outer diameter opens up the possibility of an eccentric fluid guide in the valve housing, which is advantageous for some structural designs of the valve, to the central orifice in the valve body.
  • the clamping ring is designed with the smallest possible volume.
  • the end sections of the valve housing and the valve body are provided in the covering region of the clamping ring with radial sealing edges spaced from each other, which are formed in a simple manufacturing manner by the tooth flanks of a toothing. Due to the associated with the production of the press fit of the clamping ring clawing of the clamping ring in the sealing edges in addition a positive connection is brought about and further improves the radial and axial sealing of the joint.
  • the end portions of the valve housing and the valve body at the joint abut each other and have a same outer diameter.
  • the valve body and the valve housing are in the joint with a formed on the valve body annular first stop surface and a valve housing formed on the annular second stop surface, which is preferably set back relative to the end face of the valve housing to each other.
  • the first stop surface has an inner peripheral edge which delimits a central depression acted on by the medium in the valve body
  • the second stop surface has an overhang region projecting beyond the inner peripheral edge.
  • the trough with the annular trough bottom forms an obtuse angle and is designed to be flat or concave. Through the trough, the rigidity of the valve body is reduced at the joint, and the pressure prevailing in the trough fluid pressure additionally presses the valve body radially against the clamping ring, whereby positive engagement and sealing are increased at the joint.
  • the second contact surface on the valve housing to a groove open groove is arranged, preferably a to the inner peripheral edge of the first contact surface on the valve body out at an obtuse angle to the groove bottom extending groove flank having.
  • a stiffness reduction is achieved in the end portion of the valve housing, so that the pressure prevailing in the recess and groove fluid pressure also presses the valve housing radially to the clamping ring.
  • the radial and axial sealing of the joint can be further improved by various measures.
  • the joint overlapping sealing ring made of an elastomer, such as silicone be inserted, which presses radially on the end portions of the valve housing and valve body, or at least a portion of the area covered by the clamping ring portion of the end portions of valve housing and valve body with elastic sealing material, such as silicone, be coated or between the abutting contact surfaces of the valve housing and valve body a sealing ring made of an elastomer, such as silicone, be arranged or at least one of the two contact surfaces on the valve housing and the valve body with a sealing material, such as silicone coated.
  • a welding of the clamping ring can be made on the one hand with the valve body and on the other hand with the valve housing.
  • the two welds only assume a sealing function, since the axial forces of the fluid pressure are absorbed by the clamping ring. Since the welds do not have to have high mechanical stability, it is also possible to use material for the valve housing, valve body and clamping ring which is less suitable for welding.
  • valve housing and valve body as hard as possible material with high strength, eg. B. hardened steel 1.4035, and for the clamping ring a material with high strength and slightly lower hardness, z. B. steel 1.4035 hardened and tempered used.
  • valve for metering a flowing medium ie a liquid or gaseous medium
  • a flowing medium ie a liquid or gaseous medium
  • the valve has a valve housing 11, one end of which is closed by a valve body 12.
  • a Metering 13 is formed, which is controlled by an outwardly opening valve member 14 in conjunction with a formed on the valve body 12 valve seat 122, that is closed or released.
  • valve needle 141 and one end of the valve needle 141 arranged closing head 142 having valve member 14 is actuated in a known manner by an actuator, not shown, for example, a piezoelectric actuator, against the restoring force of a valve needle 141 and the valve body 12 supporting the valve closing spring 16 ,
  • an actuator not shown, for example, a piezoelectric actuator
  • an axially extending inlet 17 for the medium is present, via which the medium in a valve body 12 coaxial with the through hole 121, the valve closing spring 16 receiving cavity 15 and from this via the valve needle 141 leading through hole 121 to the of the closed head 142 closed orifice 13 passes.
  • a joint 18 is provided, against which the mutually facing end portions of the valve housing 11 and valve body 12, which have a same outer diameter abut against each other.
  • the joint 18 is sealed by a seal 20.
  • the seal 20 has a clamping ring 19 covering the joint 18, which is press-fitted onto the end sections of valve housing 11 and valve body 12.
  • the clamping ring 19 is made of a material having a high strength and with respect to the hardness of the material of the valve housing 11 and valve body 12 slightly lower hardness.
  • the clamping ring 19 is made of steel 1.4035, hardened and tempered, and valve body 11 and valve body 12 made of steel 1.4035, hardened.
  • the interference fit is made by shrinking the clamping ring 18 onto the end portions of valve housing 11 and valve body 12.
  • the clamping ring 19 is heated, for example, inductively to the highest possible temperature, and the clamping ring 19, which is enlarged by the heating in the inner diameter, is pushed or pressed onto the end sections of valve housing 11 and valve body 12 via the joint 18.
  • the clamping ring 19 has the smallest possible volume in order to shorten its heating process and to save energy.
  • the clamping ring shrinks 19.
  • valve body 12 and valve housing 11 in the joint 18 axially contracted and between the valve body 12 and the valve housing 11 a positive connection and a radial and axial sealing produced.
  • the end portions of the valve housing 11 and valve body 12 in the overlapping region of the clamping ring 19 are additionally provided with spaced radial sealing edges, which are formed in the simplest case of the tooth flanks of a toothing 21. Due to the press fit, the clamping ring 19 additionally digs into the sealing edges of the toothing 21, whereby an additional positive connection and an increased sealing effect is achieved.
  • the radial seal and the positive connection are additionally reinforced by the pressure prevailing in the interior of valve body 12 and valve housing 11 fluid pressure that a reduction in stiffness of valve body 12 and valve housing 11 is made.
  • an annular first contact surface 22 and the valve housing 11, an annular second contact surface 23 is formed on the valve body 12.
  • First contact surface 22 and second contact surface 23 are in the joint 18 together.
  • the first contact surface 22 has an inner circumferential edge 25 delimited by a central depression 24 in the valve body 12, and the second contact surface 23, which is arranged on the valve housing 11 offset from the end face of the valve housing 11, projects beyond the inner peripheral edge 25 and thus over the depression opening 243 lying overhang 26.
  • the trough 24 has an annular trough bottom 241 through which the valve needle 141 of the valve member 14 passes, a trough wall 242 and a trough opening 243 enclosed by the trough wall 242.
  • the trough wall 242 preferably includes an obtuse angle with the trough bottom 241 and is concavely curved in the embodiment ( FIG. 2 ).
  • a flat or planar formation of the trough wall 242 is possible.
  • In Studentssteh Scheme 26 of the second bearing surface 23 on the valve housing 11 to a trough 24 open groove 27 is arranged.
  • the groove 27 has a groove flank 271 which extends toward the inner circumferential edge 25 of the first contact surface 22 on the valve body 12, preferably at an obtuse angle to the groove base 272 (FIG. FIG. 2 ).
  • the system pressure of the medium acting on the trough wall 242 and the groove flank 271 additionally presses the end sections of valve body 12 and valve housing 11 radially to the shrunk-on clamping ring 19 and thus reinforces the radial seal and the positive connection between the valve housing 11 and the valve body 12 at the joint 18th
  • the seal 20 in addition to the clamping ring 19 nor the joint 18 axially overlapping sealing ring 28 made of an elastomer, for example silicone, which is inserted into the clamping ring 19 and presses radially on the end portions of the valve housing 11 and valve body 12.
  • the sealing ring 28 is received in a groove 29 incorporated in the inner annular wall of the clamping ring 19, which is preferably arranged symmetrically with respect to the joint 18.
  • the seal 20 in addition to the clamping ring 19 nor a coating 30 made of an elastomer, such as silicone, which in the covered by the clamping ring 19 portion of the end portions of valve housing 11 and valve body 12 at least over a portion of both the end portion of the valve housing 11 as also extends the end portion of the valve body 12.
  • the two preferably equal parts of the coating 30 are applied to the end portions of valve housing 11 and valve body 12 prior to pressing the clamping ring 19.
  • the seal 20 in addition to the clamping ring 19 nor a sealing ring 31 made of an elastomer, such as silicone, which is disposed between the contact surfaces 22, 23 of the valve body 12 and the valve housing 11.
  • the seal 20 in addition to the clamping ring 19 nor a coating 32 made of an elastomer, such as silicone, which is applied to one of the two contact surfaces 22, 23 of valve body 12 and valve housing 11 or both.
  • FIG. 7 differs from the embodiment according to FIGS. 1 and 2 merely in that the clamping ring 19 which is shrunk onto the end sections of the valve housing 11 and the valve body 12 is welded at its two front ends, on the one hand, to the valve housing 11 and, on the other hand, to the valve body 12.
  • the resulting welds are in FIG. 7 denoted by 33 and 34.
  • These welds 33, 34 are used exclusively for additional sealing of the joint 18 and take no axial forces, so that their mechanical strength no higher requirements must be made and for valve housing 11, valve body 12 and clamping ring 19 less well weldable material can be used ,

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lift Valve (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Ventil zum Zumessen eines strömenden, z.B. gasförmigen oder flüssigen Mediums, insbesondere Kraftstoffeinspritzventil für Brennkraftmaschinen, nach dem Oberbegriff des Anspruchs 1.The invention is based on a valve for metering a flowing, e.g. gaseous or liquid medium, in particular fuel injection valve for internal combustion engines, according to the preamble of claim 1.

Ein bekanntes Kraftstoffeinspritzventil ( DE 10 2007 028 490A1 ) weist ein hohlzylindrisches Gehäuse mit einem zulaufseitigen und einem abspritzseitigen Ende auf. Das zulaufseitige Ende ist mit einem einen Zulaufstutzen tragenden Deckel verschlossen, und in das abspritzseitige Ende ist ein hohlzylindrischer Ventil- oder Düsenkörper eingesetzt, der teilweise aus dem Gehäuse herausragt. Am gehäusefernen Ende des Ventilkörpers ist eine Abspritzöffnung und ein die Abspritzöffnung austrittsseitig umschließender Ventilsitz ausgebildet. Das abspritzseitige Ende des Ventilgehäuses umschließt den Ventilkörper, und die zwischen Ventilgehäuse und Ventilkörper vorhandene ringförmige Fügestelle ist mittels einer Ventilgehäuse und Ventilkörper miteinander verbindenden Schweißnaht flüssigkeitsdicht abgedichtet, so dass ein im Ventilgehäuse unter Systemdruck von z.B. 200 bar stehender Kraftstoff nicht an der Fügestelle austreten kann.A known fuel injection valve ( DE 10 2007 028 490A1 ) has a hollow cylindrical housing with an inlet-side and a discharge-side end. The inflow-side end is closed by a cap carrying an inlet nozzle, and a hollow-cylindrical valve or nozzle body is inserted into the ejection-side end, which protrudes partially out of the housing. At the housing-distal end of the valve body, a spray-discharge opening and a valve seat enclosing the spray-discharge opening are formed. The discharge-side end of the valve housing encloses the valve body, and the existing between valve housing and valve body annular joint is liquid-tight sealed by a valve housing and valve body interconnecting weld, so that in the valve housing under system pressure of eg 200 bar standing fuel can not escape at the joint.

Aus der WO 01/79688 A1 ist bereits ein Ventil zum Zumessen eines strömenden, z.B. gasförmigen oder flüssigen Mediums, insbesondere Kraftstoffeinspritzventil für Brennkraftmaschinen, bekannt. Das Kraftstoffeinspritzventil hat ein einen Zulauf für das Medium aufweisendes Ventilgehäuse sowie einen eine Zumessöffnung für das Medium aufweisenden Ventilkörper, wobei zwischen dem Ventilgehäuse und dem Ventilkörper eine Fügestelle vorhanden ist und die Fügestelle von einer Dichtung abgedichtet wird. Die Dichtung weist dabei eine die Fügestelle überdeckende Spannmutter auf, die auf die beiden Bauteile Ventilgehäuse und Ventilkörper, die jeweils ein Außengewinde besitzen, mit ihrem Innengewinde aufgeschraubt ist. Auf diese Weise werden Ventilgehäuse und Ventilkörper fest miteinander verbunden und sitzen im Bereich der Fügestelle fest verschraubt aufeinander auf. Die Spannmutter dient der Verspannung von Ventilgehäuse und Ventilkörper mittels einer Schraubverbindung. Bei dem Kraftstoffeinspritzventil handelt es sich um einen Dieselinjektor, mit dem bekannterweise Dieselkraftstoff mit Drücken weit über 1000 bar direkt in den Brennraum von Dieselmotoren eingespritzt wird, weshalb bei dieser Bauart von Injektoren aus Festigkeitsgründen Schraubverbindungen zum Einsatz kommen.From the WO 01/79688 A1 is already a valve for metering a flowing, for example, gaseous or liquid medium, in particular fuel injection valve for internal combustion engines, known. The fuel injection valve has a valve housing having an inlet for the medium and a valve body having an orifice for the medium, wherein a joint is present between the valve housing and the valve body and the joint is sealed by a seal. The seal has a joint covering the clamping nut, which is screwed onto the two components valve housing and valve body, each having an external thread with its internal thread. In this way, valve body and valve body are firmly connected and sit tightly screwed together in the joint area. The clamping nut serves to clamp the valve housing and valve body by means of a screw connection. The fuel injection valve is a diesel injector with which, as is known, diesel fuel is injected at pressures well above 1000 bar directly into the combustion chamber of diesel engines, which is why bolted connections are used in this type of injector for reasons of strength.

Aus der DE 197 05 227 A1 ist bereits ein Kraftstoffeinspritzventil für Brennkraftmaschinen bekannt, das mit einem einen Zulauf für das abzuspritzende Medium aufweisenden Ventilgehäuse, mit einem eine Zumessöffnung für das Medium aufweisenden Ventilkörper, mit einer zwischen Ventilgehäuse und Ventilkörper vorhandenen Fügestelle und mit einer die Fügestelle abdichtenden Dichtung ausgestattet ist. Die Dichtung weist eine die Fügestelle überdeckende Spannhülse auf, die nach einem Fügevorgang mittels eines Ziehrings kraftschlüssig in eine Vertiefung des Ventilgehäuses mit einer Wulst eingreift.From the DE 197 05 227 A1 a fuel injection valve for internal combustion engines is already known, which is equipped with a valve housing having a feed for the medium to be injected, with a valve body having an orifice for the medium, with a joint present between the valve housing and the valve body and with a seal sealing the joint. The seal has a joint covering the clamping sleeve, which engages by a joining operation by means of a drawing ring frictionally engages in a recess of the valve housing with a bead.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Ventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass durch den mit Presssitz auf Ventilgehäuse und Ventilkörper die Fügestelle überdeckenden Klemmring eine im Vergleich zu einer Schweißnaht sichere und rissunanfällige Abdichtung der Fügestelle zwischen Ventilgehäuse und Ventilkörper hergestellt ist. Der Presssitz des Klemmrings wird vorzugsweise durch Aufschrumpfen hergestellt. Hierzu wird der Klemmring, z. B. induktiv und auf möglichst hohe Temperaturen, erwärmt und der dadurch im Innendurchmesser aufgeweitete Klemmring auf die Endabschnitte von Ventilgehäuse und Ventilkörper die Fügestelle überdeckend aufgeschoben oder aufgepresst. Der Klemmring schrumpft bei Abkühlung und zieht den Ventilkörper und das Ventilgehäuse axial zusammen, wodurch zwischen Ventilgehäuse und Ventilkörper Kraftschluss und eine radiale und axiale Abdichtung der Fügestelle herbeigeführt wird. Alternativ kann der Presssitz auch durch mechanisches Aufpressen des auf die Endabschnitte von Ventilgehäuse und Ventilkörper mit Übermaß aufgeschobenen Klemmrings hergestellt werden. Das Material von Ventilgehäuse und Ventilkörper kann - anders als bei einer Abdichtung durch eine Schweißnaht - frei gewählt werden, da der Zwang zur Verwendung eines sehr gut schweißfähigen Materials zur Erzielung einer mechanisch stabilen, druck- und reißfesten Schweißnaht entfällt. Somit können Ventilgehäuse und Ventilkörper aus kostengünstigem Werkstoff hergestellt und die Herstellkosten gesenkt werden. Anders als beim Schweißen, wo ein Schweißverzug zwischen Ventilgehäuse und Ventilkörper auftreten kann, wird eine zuverlässige und gute Lagepositionierung der beiden Teile erzielt. Anders als bei einer Verschweißung von Ventilgehäuse und Ventilkörper kann eine zuverlässige Abdichtung der Fügestelle auch bei einem großen Außendurchmesser des Ventilkörpers trotz großer Drücke im Ventilgehäuse gewährleistet werden. Ein großer Außendurchmesser wiederum eröffnet die Möglichkeit einer für einige konstruktiven Ausführungen des Ventils vorteilhaften, exzentrischen Fluidführung im Ventilgehäuse zu der zentralen Zumessöffnung im Ventilkörper. Um den Energieeinsatz zum Erhitzen des Klemmrings zu beschränken, ist der Klemmring mit einem möglichst kleinen Volumen ausgelegt.The valve according to the invention with the features of claim 1 has the advantage that a secure and rissunanfällige sealing of the joint between the valve housing and the valve body is made by the interference fit on the valve body and valve body the joint overlapping clamping ring in comparison to a weld. The interference fit of the clamping ring is preferably produced by shrinking. For this purpose, the clamping ring, z. B. inductive and to the highest possible temperatures, heated and thereby expanded in the inner diameter clamping ring on the end portions of the valve housing and the valve body, the joint pushed over or pressed overlapping. The clamping ring shrinks when cooled and pulls the valve body and the valve housing axially together, whereby between valve body and valve body traction and a radial and axial sealing of the joint is brought about. Alternatively, the interference fit can also be produced by mechanically pressing on the clamping ring pushed onto the end sections of the valve housing and valve body in excess. The material of valve housing and valve body can - unlike a seal by a weld - are freely chosen, since the compulsion to use a very good weldable material to achieve a mechanically stable, pressure and tear resistant weld is eliminated. Thus, valve body and valve body can be made of inexpensive material and the production costs are reduced. Unlike welding, where a welding distortion between the valve body and valve body may occur, a reliable and good positional positioning of the two parts is achieved. Unlike a welding of valve housing and valve body, a reliable sealing of the joint can be ensured even with a large outer diameter of the valve body despite high pressures in the valve housing. In turn, a large outer diameter opens up the possibility of an eccentric fluid guide in the valve housing, which is advantageous for some structural designs of the valve, to the central orifice in the valve body. To limit the energy used to heat the clamping ring, the clamping ring is designed with the smallest possible volume.

Erfindungsgemäß sind die Endabschnitte von Ventilgehäuse und Ventilkörper im Überdeckungsbereich des Klemmrings mit voneinander beabstandeten radialen Dichtungskanten versehen, die in fertigungstechnisch einfacher Weise von den Zahnflanken einer Verzahnung gebildet sind. Durch die mit der Herstellung des Presssitzes des Klemmrings einhergehende Verkrallung des Klemmrings in den Dichtungskanten wird zusätzlich ein Formschluss herbeigeführt und die radiale und axiale Abdichtung der Fügestelle weiter verbessert.According to the invention, the end sections of the valve housing and the valve body are provided in the covering region of the clamping ring with radial sealing edges spaced from each other, which are formed in a simple manufacturing manner by the tooth flanks of a toothing. Due to the associated with the production of the press fit of the clamping ring clawing of the clamping ring in the sealing edges in addition a positive connection is brought about and further improves the radial and axial sealing of the joint.

Durch die in den weiten Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Ventils möglich.The measures listed in the broad claims advantageous refinements and improvements of the claim 1 valve are possible.

Gemäß einer vorteilhaften Ausführungsform der Erfindung liegen die Endabschnitte von Ventilgehäuse und Ventilkörper an der Fügestelle auf Stoß aneinander und weisen einen gleichen Außendurchmesser auf. Dabei liegen Ventilkörper und Ventilgehäuse in der Fügestelle mit einer am Ventilkörper ausgebildeten ringförmigen ersten Anschlagfläche und einer am Ventilgehäuse ausgebildeten ringförmigen zweiten Anschlagfläche, die vorzugsweise gegenüber der Stirnseite des Ventilgehäuses zurückversetzt angeordnet ist, aneinander. Die erste Anschlagfläche weist eine innere Umlaufkante, die eine vom Medium beaufschlagte, zentrale Mulde im Ventilkörper begrenzt, und die zweite Anschlagfläche einen über die innere Umlaufkante vorspringenden Überstehbereich auf. Dabei schließt die Mulde mit dem ringförmigen Muldenboden einen stumpfen Winkel ein und ist eben oder konkav gewölbt ausgebildet. Durch die Mulde wird die Steifigkeit des Ventilkörpers an der Fügestelle reduziert, und der in der Mulde herrschende Fluiddruck presst zusätzlich den Ventilkörper radial gegen den Klemmring, wodurch Formschluss und Abdichtung an der Fügestelle erhöht werden.According to an advantageous embodiment of the invention, the end portions of the valve housing and the valve body at the joint abut each other and have a same outer diameter. In this case, the valve body and the valve housing are in the joint with a formed on the valve body annular first stop surface and a valve housing formed on the annular second stop surface, which is preferably set back relative to the end face of the valve housing to each other. The first stop surface has an inner peripheral edge which delimits a central depression acted on by the medium in the valve body, and the second stop surface has an overhang region projecting beyond the inner peripheral edge. In this case, the trough with the annular trough bottom forms an obtuse angle and is designed to be flat or concave. Through the trough, the rigidity of the valve body is reduced at the joint, and the pressure prevailing in the trough fluid pressure additionally presses the valve body radially against the clamping ring, whereby positive engagement and sealing are increased at the joint.

Dieser Effekt wird noch dadurch gesteigert, dass gemäß einer weiteren Ausführungsform der Erfindung im Überstehbereich der zweiten Anlagefläche am Ventilgehäuse eine zur Mulde hin offene Nut angeordnet ist, die vorzugsweise eine zur inneren Umlaufkante der ersten Anlagefläche am Ventilkörper hin unter einem stumpfen Winkel zum Nutgrund verlaufende Nutflanke aufweist. Durch diese Nut wird auch im Endabschnitt des Ventilgehäuses eine Steifigkeitsreduzierung erreicht, so dass der in Mulde und Nut herrschende Fluiddruck auch das Ventilgehäuse radial an den Klemmring anpresst.This effect is further enhanced by the fact that according to a further embodiment of the invention in the Überstehbereich the second contact surface on the valve housing to a groove open groove is arranged, preferably a to the inner peripheral edge of the first contact surface on the valve body out at an obtuse angle to the groove bottom extending groove flank having. Through this groove a stiffness reduction is achieved in the end portion of the valve housing, so that the pressure prevailing in the recess and groove fluid pressure also presses the valve housing radially to the clamping ring.

Gemäß weiterer Ausführungsformen der Erfindung lässt sich die radiale und axiale Abdichtung der Fügestelle durch verschiedene Maßnahmen zusätzlich verbessern. So kann noch im Klemmring ein die Fügestelle überdeckender Dichtungsring aus einem Elastomer, z.B. Silikon, eingelegt sein, der sich radial auf die Endabschnitte von Ventilgehäuse und Ventilkörper aufpresst, oder zumindest ein Teil des vom Klemmring überdeckten Bereichs der Endabschnitte von Ventilgehäuse und Ventilkörper mit elastischem Dichtungsmaterial, z.B. Silikon, beschichtet sein oder zwischen den aneinanderliegenden Anlageflächen von Ventilgehäuse und Ventilkörper eine Dichtungsring aus einem Elastomer, z.B. Silikon, angeordnet sein oder mindestens eine der beiden Anlageflächen an Ventilgehäuse und Ventilkörper mit einem Dichtungsmaterial, z.B. Silikon, beschichtet sein. Im übrigen kann zusätzlich eine Verschweißung des Klemmrings einerseits mit dem Ventilkörper und andererseits mit dem Ventilgehäuse vorgenommen werden. In diesem Fall übernehmen die beiden Schweißnähte nur eine Dichtungsfunktion, da die axialen Kräfte des Fluiddrucks vom Klemmring aufgenommen werden. Da dadurch die Schweißnähte keine hohe mechanische Stabilität besitzen müssen, kann für Ventilgehäuse, Ventilkörper und Klemmring auch Material eingesetzt werden, das weniger gut zum Schweißen geeignet ist.According to further embodiments of the invention, the radial and axial sealing of the joint can be further improved by various measures. Thus, even in the clamping ring, the joint overlapping sealing ring made of an elastomer, such as silicone, be inserted, which presses radially on the end portions of the valve housing and valve body, or at least a portion of the area covered by the clamping ring portion of the end portions of valve housing and valve body with elastic sealing material, such as silicone, be coated or between the abutting contact surfaces of the valve housing and valve body a sealing ring made of an elastomer, such as silicone, be arranged or at least one of the two contact surfaces on the valve housing and the valve body with a sealing material, such as silicone coated. Moreover, in addition, a welding of the clamping ring can be made on the one hand with the valve body and on the other hand with the valve housing. In this case, the two welds only assume a sealing function, since the axial forces of the fluid pressure are absorbed by the clamping ring. Since the welds do not have to have high mechanical stability, it is also possible to use material for the valve housing, valve body and clamping ring which is less suitable for welding.

Vorzugsweise wird für Ventilgehäuse und Ventilkörper ein möglichst harter Werkstoff mit hoher Festigkeit, z. B. Stahl 1.4035 gehärtet, und für den Klemmring ein Wekstoff mit hoher Festigkeit und leicht geringerer Härte, z. B. Stahl 1.4035 gehärtet und angelassen, eingesetzt.Preferably, the valve housing and valve body as hard as possible material with high strength, eg. B. hardened steel 1.4035, and for the clamping ring a material with high strength and slightly lower hardness, z. B. steel 1.4035 hardened and tempered used.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die Erfindung ist anhand von in den Zeichnungen dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

  • Figur 1 ausschnittweise einen Längsschnitt eines Ventils zum Zumessen eines flüssigen oder gasförmigen Mediums,
  • Figur 3 bis 7 jeweils eine gleiche Darstellung wie in Figur 2 gemäß weiterer Ausführungsbeispiele.
The invention is explained in more detail in the following description with reference to exemplary embodiments illustrated in the drawings. Show it:
  • FIG. 1 1 in a section of a longitudinal section of a valve for metering a liquid or gaseous medium,
  • FIGS. 3 to 7 each a same representation as in FIG. 2 according to further embodiments.

Das in Figur 1 im Längsschnitt dargestellte Ventil zum Zumessen eines strömenden Mediums, also eines flüssigen oder gasfförmigen Mediums, wird vorzugsweise als Einspritzventil zum Einspritzen von Kraftstoff in den Verbrennungszylinder oder Luftansaugtrakt einer Brennkraftmaschinen eingesetzt, kann aber auch als Dosierventil zum Einspritzen einer wässrigen Lösung, wie z.B. einer Harnstoff-Wasser-Lösung, in den Abgasstrang einer Brennkraftmaschinen herangezogen werden. Das Ventil weist ein Ventilgehäuse 11 auf, dessen eines Stirnende von einem Ventilkörper 12 abgeschlossen ist. Am gehäusefernen Ende einer zentral im Ventilkörper 12 verlaufenden Durchgangsbohrung 121 ist eine Zumessöffnung 13 ausgebildet, die von einem nach außen öffnenden Ventilglied 14 in Verbindung mit einem am Ventilkörper 12 ausgebildeten Ventilsitz 122 gesteuert, also geschlossen oder freigegeben wird. Das eine Ventilnadel 141 und einen endseitig an der Ventilnadel 141 angeordneten Schließkopf 142 aufweisende Ventilglied 14 wird in bekannter Weise von einem hier nicht dargestellten Aktor, z.B. einem piezoelektrischen Aktor, gegen die Rückstellkraft einer an der Ventilnadel 141 und am Ventilkörper 12 sich abstützenden Ventilschließfeder 16 betätigt. Im Ventilgehäuse 11 ist exzentrisch ein axial verlaufender Zulauf 17 für das Medium vorhanden, über den das Medium in einen im Ventilkörper 12 koaxial zur Durchgangsbohrung 121 ausgebildeten, die Ventilschließfeder 16 aufnehmenden Hohlraum 15 und von diesem über die die Ventilnadel 141 führende Durchgangsbohrung 121 zu der von dem Schließkopf 142 geschlossenen Zumessöffnung 13 gelangt.This in FIG. 1 in longitudinal section shown valve for metering a flowing medium, ie a liquid or gaseous medium, is preferably used as an injector for injecting fuel into the combustion cylinder or air intake tract of an internal combustion engine, but can also be used as a metering valve for injecting an aqueous solution, such as a urea Water solution, are used in the exhaust system of an internal combustion engine. The valve has a valve housing 11, one end of which is closed by a valve body 12. At the housing distal end of a centrally extending in the valve body 12 through bore 121 is a Metering 13 is formed, which is controlled by an outwardly opening valve member 14 in conjunction with a formed on the valve body 12 valve seat 122, that is closed or released. The one valve needle 141 and one end of the valve needle 141 arranged closing head 142 having valve member 14 is actuated in a known manner by an actuator, not shown, for example, a piezoelectric actuator, against the restoring force of a valve needle 141 and the valve body 12 supporting the valve closing spring 16 , In the valve housing 11, an axially extending inlet 17 for the medium is present, via which the medium in a valve body 12 coaxial with the through hole 121, the valve closing spring 16 receiving cavity 15 and from this via the valve needle 141 leading through hole 121 to the of the closed head 142 closed orifice 13 passes.

Zwischen Ventilgehäuse 11 und Ventilkörper 12 ist eine Fügestelle 18 vorhanden, an der die einander zugekehrten Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12, die einen gleichen Außendurchmesser aufweisen, auf Stoß aneinanderliegen. Die Fügestelle 18 ist durch eine Dichtung 20 abgedichtet. Die Dichtung 20 weist erfindungsgemäß einen die Fügestelle 18 überdeckenden Klemmring 19 auf, der mit Presssitz auf den Endabschnitten von Ventilgehäuse 11 und Ventilkörper 12 aufsitzt. Der Klemmring 19 ist aus einem Werkstoff mit einer hohen Festigkeit und einer gegenüber der Härte des Werkstoffs von Ventilgehäuse 11 und Ventilkörper 12 leicht geringeren Härte. Z. B. ist der Klemmring 19 aus Stahl 1.4035, gehärtet und angelassen, und Ventilgehäuse 11 und Ventilkörper 12 aus Stahl 1.4035, gehärtet.Between the valve housing 11 and the valve body 12, a joint 18 is provided, against which the mutually facing end portions of the valve housing 11 and valve body 12, which have a same outer diameter abut against each other. The joint 18 is sealed by a seal 20. According to the invention, the seal 20 has a clamping ring 19 covering the joint 18, which is press-fitted onto the end sections of valve housing 11 and valve body 12. The clamping ring 19 is made of a material having a high strength and with respect to the hardness of the material of the valve housing 11 and valve body 12 slightly lower hardness. For example, the clamping ring 19 is made of steel 1.4035, hardened and tempered, and valve body 11 and valve body 12 made of steel 1.4035, hardened.

Vorzugsweise wird der Presssitz durch Aufschrumpfen des Klemmrings 18 auf die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 hergestellt. Der Klemmring 19 wird hierzu, vorzugsweise z.B. induktiv auf möglichst hohe Temperatur, erwärmt und der durch die Erwärmung im Innendurchmesser vergrößerte Klemmring 19 auf die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 über die Fügestelle 18 hinweg aufgeschoben oder aufgepresst. Der Klemmring 19 weist zwecks Verkürzung seines Erwärmungsprozesses und zur Energieeinsparung ein möglichst kleines Volumen auf. Beim Abkühlen schrumpft der Klemmring 19. Dabei werden Ventilkörper 12 und Ventilgehäuse 11 in der Fügestelle 18 axial zusammengezogen und zwischen Ventilkörper 12 und Ventilgehäuse 11 ein Kraftschluss und eine radiale und axiale Abdichtung hergestellt.Preferably, the interference fit is made by shrinking the clamping ring 18 onto the end portions of valve housing 11 and valve body 12. For this purpose, the clamping ring 19 is heated, for example, inductively to the highest possible temperature, and the clamping ring 19, which is enlarged by the heating in the inner diameter, is pushed or pressed onto the end sections of valve housing 11 and valve body 12 via the joint 18. The clamping ring 19 has the smallest possible volume in order to shorten its heating process and to save energy. Upon cooling, the clamping ring shrinks 19. In this case, valve body 12 and valve housing 11 in the joint 18 axially contracted and between the valve body 12 and the valve housing 11 a positive connection and a radial and axial sealing produced.

Wie aus dem in Figur 2 vergrößert dargestellten Ausschnitt des Ventils zu erkennen ist, sind die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 im Überdeckungsbereich des Klemmrings 19 zusätzlich mit voneinander beabstandeten radialen Dichtungskanten versehen, die im einfachsten Fall von den Zahnflanken einer Verzahnung 21 gebildet sind. Durch den Presssitz verkrallt sich der Klemmring 19 zusätzlich in den Dichtungskanten der Verzahnung 21, wodurch ein zusätzlicher Formschluss und eine gesteigerte Dichtwirkung erzielt wird.As from the in FIG. 2 enlarged section of the valve can be seen, the end portions of the valve housing 11 and valve body 12 in the overlapping region of the clamping ring 19 are additionally provided with spaced radial sealing edges, which are formed in the simplest case of the tooth flanks of a toothing 21. Due to the press fit, the clamping ring 19 additionally digs into the sealing edges of the toothing 21, whereby an additional positive connection and an increased sealing effect is achieved.

Die radiale Abdichtung und der Formschluss werden durch den im Innern von Ventilkörper 12 und Ventilgehäuse 11 herrschenden Fluiddruck zusätzlich dadurch verstärkt, dass eine Steifigkeitsreduzierung von Ventilkörper 12 und Ventilgehäuse 11 vorgenommen ist. Hierzu ist am Ventilkörper 12 eine ringförmige erste Anlagefläche 22 und am Ventilgehäuse 11 eine ringförmige zweite Anlagefläche 23 ausgebildet. Erste Anlagefläche 22 und zweite Anlagefläche 23 liegen in der Fügestelle 18 aneinander. Die erste Anlagefläche 22 weist eine von einer zentralen Mulde 24 im Ventilkörper 12 begrenzte innere Umlaufkante 25 und die zweite Anlagefläche 23, die am Ventilgehäuse 11 gegenüber der Stirnseite des Ventilgehäuses 11 zurückversetzt angeordnet ist, einen über die innere Umlaufkante 25 vorstehenden und damit über der Muldenöffnung 243 liegenden Überstehbereich 26 auf. Die Mulde 24 hat einen ringförmigen Muldenboden 241, durch den die Ventilnadel 141 des Ventilglieds 14 hindurchtritt, eine Muldenwand 242 und eine von der Muldenwand 242 umschlossene Muldenöffnung 243. In die Muldenöffnung 243 mündet der Zulauf 17 für das Medium, so dass die Mulde 24 von unter Systemdruck stehendem Medium beaufschlagt ist. Die Muldenwand 242 schließt vorzugsweise mit dem Muldenboden 241 einen stumpfen Winkel ein und ist im Ausführungsbeispiel konkav gewölbt ausgebildet (Figur 2). Eine ebene oder plane Ausbildung der Muldenwand 242 ist möglich. Im Überstehbereich 26 der zweiten Anlagefläche 23 am Ventilgehäuse 11 ist eine zur Mulde 24 hin offene Nut 27 angeordnet. Die Nut 27 weist eine Nutflanke 271 auf, die zur inneren Umlaufkante 25 der ersten Anlagefläche 22 am Ventilkörper 12 hin, vorzugsweise unter einem stumpfen Winkel zum Nutgrund 272, verläuft (Figur 2). Der auf die Muldenwand 242 und die Nutflanke 271 wirkende Systemdruck des Mediums presst zusätzlich die Endabschnitte von Ventilkörper 12 und Ventilgehäuse 11 radial an den aufgeschrumpften Klemmring 19 an und verstärkt somit die radiale Abdichtung und den Formschluss zwischen Ventilgehäuse 11 und Ventilkörper 12 an der Fügestelle 18.The radial seal and the positive connection are additionally reinforced by the pressure prevailing in the interior of valve body 12 and valve housing 11 fluid pressure that a reduction in stiffness of valve body 12 and valve housing 11 is made. For this purpose, an annular first contact surface 22 and the valve housing 11, an annular second contact surface 23 is formed on the valve body 12. First contact surface 22 and second contact surface 23 are in the joint 18 together. The first contact surface 22 has an inner circumferential edge 25 delimited by a central depression 24 in the valve body 12, and the second contact surface 23, which is arranged on the valve housing 11 offset from the end face of the valve housing 11, projects beyond the inner peripheral edge 25 and thus over the depression opening 243 lying overhang 26. The trough 24 has an annular trough bottom 241 through which the valve needle 141 of the valve member 14 passes, a trough wall 242 and a trough opening 243 enclosed by the trough wall 242. In the trough opening 243, the inlet 17 for the medium opens, so that the trough 24 of FIG pressurized medium under system pressure is applied. The trough wall 242 preferably includes an obtuse angle with the trough bottom 241 and is concavely curved in the embodiment ( FIG. 2 ). A flat or planar formation of the trough wall 242 is possible. In Überstehbereich 26 of the second bearing surface 23 on the valve housing 11 to a trough 24 open groove 27 is arranged. The groove 27 has a groove flank 271 which extends toward the inner circumferential edge 25 of the first contact surface 22 on the valve body 12, preferably at an obtuse angle to the groove base 272 (FIG. FIG. 2 ). The system pressure of the medium acting on the trough wall 242 and the groove flank 271 additionally presses the end sections of valve body 12 and valve housing 11 radially to the shrunk-on clamping ring 19 and thus reinforces the radial seal and the positive connection between the valve housing 11 and the valve body 12 at the joint 18th

In den in Figur 3 bis 7 dargestellten Ausschnitten von modifizierten Ausführungsbeispielen des Ventils ist die Dichtung 20 an der Fügestelle 18 zwischen Ventilgehäuse 11 und Ventilkörper 12 zusätzlich zu dem aufgeschrumpften Klemmring 19 noch durch weitere konstruktive Maßnahmen ergänzt.In the in FIGS. 3 to 7 shown sections of modified embodiments of the valve, the seal 20 at the joint 18 between the valve housing 11 and valve body 12 in addition to the shrunk-clamping ring 19 is supplemented by further design measures.

In dem Ausführungsbeispiel gemäß Figur 3 weist die Dichtung 20 zusätzlich zu dem Klemmring 19 noch einen die Fügestelle 18 axial überdeckenden Dichtungsring 28 aus einem Elastomer, z.B. Silikon auf, der in den Klemmring 19 eingelegt ist und sich radial auf die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 aufpresst. Der Dichtungsring 28 ist in einer in die innere Ringwand des Klemmrings 19 eingearbeiteten Nut 29 aufgenommen, die vorzugsweise symmetrisch zur Fügestelle 18 angeordnet ist.In the embodiment according to FIG. 3 the seal 20 in addition to the clamping ring 19 nor the joint 18 axially overlapping sealing ring 28 made of an elastomer, for example silicone, which is inserted into the clamping ring 19 and presses radially on the end portions of the valve housing 11 and valve body 12. The sealing ring 28 is received in a groove 29 incorporated in the inner annular wall of the clamping ring 19, which is preferably arranged symmetrically with respect to the joint 18.

In dem Ausführungsbeispiel gemäß Figur 4 weist die Dichtung 20 zusätzlich zu dem Klemmring 19 noch eine Beschichtung 30 aus einem Elastomer, z.B. Silikon, auf, die sich in dem vom Klemmring 19 überdeckten Bereich der Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 zumindest über einen Teil sowohl des Endabschnitts von Ventilgehäuse 11 als auch des Endabschnitts von Ventilkörper 12 erstreckt. Die beiden vorzugsweise gleich großen Teile der Beschichtung 30 werden vor dem Aufpressen des Klemmrings 19 auf die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 aufgetragen.In the embodiment according to FIG. 4 the seal 20 in addition to the clamping ring 19 nor a coating 30 made of an elastomer, such as silicone, which in the covered by the clamping ring 19 portion of the end portions of valve housing 11 and valve body 12 at least over a portion of both the end portion of the valve housing 11 as also extends the end portion of the valve body 12. The two preferably equal parts of the coating 30 are applied to the end portions of valve housing 11 and valve body 12 prior to pressing the clamping ring 19.

In dem Ausführungsbeispiel gemäß Figur 5 weist die Dichtung 20 zusätzlich zu dem Klemmring 19 noch einen Dichtungsring 31 aus einem Elastomer, z.B. Silikon, auf, der zwischen den Anlageflächen 22, 23 von Ventilkörper 12 und Ventilgehäuse 11 angeordnet ist.In the embodiment according to FIG. 5 the seal 20 in addition to the clamping ring 19 nor a sealing ring 31 made of an elastomer, such as silicone, which is disposed between the contact surfaces 22, 23 of the valve body 12 and the valve housing 11.

In dem Ausführungsbeispiel gemäß Figur 6 weist die Dichtung 20 zusätzlich zu dem Klemmring 19 noch eine Beschichtung 32 aus einem Elastomer, z.B. Silikon, auf, die auf eine der beiden Anlageflächen 22, 23 von Ventilkörper 12 und Ventilgehäuse 11 oder auf beide aufgetragen ist.In the embodiment according to FIG. 6 the seal 20 in addition to the clamping ring 19 nor a coating 32 made of an elastomer, such as silicone, which is applied to one of the two contact surfaces 22, 23 of valve body 12 and valve housing 11 or both.

Das Ausführungsbeispiel gemäß Figur 7 unterscheidet sich von dem Ausführungsbeispiel gemäß Figur 1 und 2 lediglich dadurch, dass der auf die Endabschnitte von Ventilgehäuse 11 und Ventilkörper 12 aufgeschrumpfte Klemmring 19 noch an seinen beiden Stirnenden einerseits mit dem Ventilgehäuse 11 und andererseits mit dem Ventilkörper 12 verschweißt ist. Die hierbei entstehenden Schweißnähte sind in Figur 7 mit 33 und 34 bezeichnet. Diese Schweißnähte 33, 34 dienen ausschließlich zur zusätzlichen Abdichtung der Fügestelle 18 und nehmen keine axialen Kräfte auf, so dass an ihrer mechanischen Festigkeit keine höheren Anforderungen gestellt werden müssen und für Ventilgehäuse 11, Ventilkörper 12 und Klemmring 19 auch weniger gut schweißbarer Werkstoff verwendet werden kann.The embodiment according to FIG. 7 differs from the embodiment according to FIGS. 1 and 2 merely in that the clamping ring 19 which is shrunk onto the end sections of the valve housing 11 and the valve body 12 is welded at its two front ends, on the one hand, to the valve housing 11 and, on the other hand, to the valve body 12. The resulting welds are in FIG. 7 denoted by 33 and 34. These welds 33, 34 are used exclusively for additional sealing of the joint 18 and take no axial forces, so that their mechanical strength no higher requirements must be made and for valve housing 11, valve body 12 and clamping ring 19 less well weldable material can be used ,

Bis auf die modifizierte Dichtung 20 stimmen die in Figur 3 bis 7 ausschnittweise dargestellten Ausführungsbeispiele der Ventile mit dem Ausführungsbeispiel des Ventils gemäß Figur 1 und 2 überein, so dass gleiche Bauteile mit gleichen Bezugszeichen versehen sind.Except for the modified seal 20 vote in FIGS. 3 to 7 partially illustrated embodiments of the valves with the embodiment of the valve according to FIGS. 1 and 2 match, so that the same components are provided with the same reference numerals.

Claims (13)

  1. Valve for metering in a flowing, for example gaseous or liquid medium, in particular fuel injection valve for internal combustion engines, having a valve housing (11) which has an inflow (17) for the medium, having a valve body (12) which has a metering-in opening (13) for the medium, having a join (18) which is present between the valve housing (11) and the valve body (12), and having a seal (20) which seals the join (18), characterized in that the seal (20) has a clamping ring (19) which covers the join (18) and is seated with a press fit on end sections of the valve housing (11) and the valve body (12), which end sections face one another at the join (18), the press fit being produced by way of shrinking or by way of mechanical pressing of the clamping ring (19) onto the end sections of the valve housing (11) and the valve body (12), and, in the covering region of the clamping ring (19), the end sections of the valve housing (11) and the valve body (12) being provided with radial seal edges which are spaced apart from one another, and the radial seal edges being formed here by the tooth flanks of a toothing system (21).
  2. Valve according to Claim 1, characterized in that the end sections of the valve housing (11) and the valve body (12) bear against one another in an abutting manner at the join (18) and have an identical external diameter.
  3. Valve according to Claim 2, characterized in that the valve body (12) and the valve housing (11) bear against one another in the join (18) by way of an annular first bearing face (22) which is configured on the valve body (12) and an annular second bearing face (23) which is configured on the valve housing (11), and in that the first bearing face (22) has an inner circumferential edge (25) which delimits a central recess (24) in the valve body (12), which central recess (24) is loaded by the medium, and the second bearing face (23) has a projecting region (26) which protrudes beyond the inner circumferential edge (25).
  4. Valve according to Claim 3, characterized in that the recess (24) has an annular recess bottom (241), a recess wall (242) and a recess opening (243) which is enclosed by the recess wall (242) and into which the inflow (17) for the medium opens, and preferably in that the recess wall (242) encloses an obtuse angle with the recess bottom (241) and is of planar or concavely curved configuration.
  5. Valve according to Claim 3 or 4, characterized in that a groove (27) which is open towards the recess (24) is arranged in the projection region of the second bearing face (23) on the valve housing (11).
  6. Valve according to Claim 5, characterized in that the groove (27) has a groove flank (271) which runs at an obtuse angle with respect to the groove bottom (272) towards the inner circumferential edge (25) of the first bearing face (22) on the valve body (12).
  7. Valve according to one of Claims 3 to 6, characterized in that the second bearing face (23) on the valve housing (11) is arranged set back with respect to the end side of the valve housing (11).
  8. Valve according to one of Claims 1 to 7, characterized in that the seal (20) has a seal ring (28) which covers the join (18) axially, is made from an elastomer, for example silicone, is inserted into the clamping ring (19), and is pressed radially onto the end sections of the valve housing (11) and the valve body (12) .
  9. Valve according to Claim 8, characterized in that the seal ring (28) is received in a groove (29) which is machined into the inner annular wall of the clamping ring (19).
  10. Valve according to one of Claims 1 to 7, characterized in that the seal (20) has a coating (30) which is made from an elastomer, for example silicone, and coats at least one part of that region of the end sections of the valve housing (11) and the valve body (12) which is covered by the clamping ring (19).
  11. Valve according to one of Claims 3 to 7, characterized in that the seal (20) has a seal ring (21) which is made from an elastomer, for example silicone, and is arranged between the bearing faces (22, 23) of the valve body (12) and the valve housing (11).
  12. Valve according to one of Claims 3 to 7, characterized in that the seal (20) has a coating (30) which is made from an elastomer, for example silicone, and coats at least one of the two bearing faces (22, 23) on the valve body (12) and the valve housing (11).
  13. Valve according to one of Claims 1 to 12, characterized in that the clamping ring (15) is welded on the end side firstly to the valve housing (11) and secondly to the valve body (12).
EP12729163.1A 2011-08-18 2012-06-26 Valve for dosing a flowing medium Not-in-force EP2745002B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011081176A DE102011081176A1 (en) 2011-08-18 2011-08-18 Valve for metering a flowing medium
PCT/EP2012/062303 WO2013023825A1 (en) 2011-08-18 2012-06-26 Valve for dosing a flowing medium

Publications (2)

Publication Number Publication Date
EP2745002A1 EP2745002A1 (en) 2014-06-25
EP2745002B1 true EP2745002B1 (en) 2018-12-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12729163.1A Not-in-force EP2745002B1 (en) 2011-08-18 2012-06-26 Valve for dosing a flowing medium

Country Status (7)

Country Link
US (1) US9976531B2 (en)
EP (1) EP2745002B1 (en)
JP (1) JP6033306B2 (en)
KR (1) KR20140049556A (en)
CN (1) CN103748350A (en)
DE (1) DE102011081176A1 (en)
WO (1) WO2013023825A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3139030A1 (en) * 2015-09-03 2017-03-08 Continental Automotive GmbH Injector for a combustion engine
WO2018135262A1 (en) * 2017-01-23 2018-07-26 日立オートモティブシステムズ株式会社 Fuel injection valve

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Also Published As

Publication number Publication date
KR20140049556A (en) 2014-04-25
CN103748350A (en) 2014-04-23
EP2745002A1 (en) 2014-06-25
US20140299805A1 (en) 2014-10-09
JP2014521883A (en) 2014-08-28
DE102011081176A1 (en) 2013-02-21
JP6033306B2 (en) 2016-11-30
WO2013023825A1 (en) 2013-02-21
US9976531B2 (en) 2018-05-22

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