EP2766593A1 - Hydraulic coupling - Google Patents

Hydraulic coupling

Info

Publication number
EP2766593A1
EP2766593A1 EP12770055.7A EP12770055A EP2766593A1 EP 2766593 A1 EP2766593 A1 EP 2766593A1 EP 12770055 A EP12770055 A EP 12770055A EP 2766593 A1 EP2766593 A1 EP 2766593A1
Authority
EP
European Patent Office
Prior art keywords
spring
pot
membrane
hydraulic coupler
coupler according
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.)
Granted
Application number
EP12770055.7A
Other languages
German (de)
French (fr)
Other versions
EP2766593B1 (en
Inventor
Dietmar SCHMIEDERER
Thomas Sebastian
Andreas Jakobi
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2766593A1 publication Critical patent/EP2766593A1/en
Application granted granted Critical
Publication of EP2766593B1 publication Critical patent/EP2766593B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8023—Fuel injection apparatus manufacture, repair or assembly the assembly involving use of quick-acting mechanisms, e.g. clips

Definitions

  • a known fuel injection valve (DE 10 2004 002 134 A1) has a between a valve needle and a piezoelectric actuator axially clamped hydraulic coupler having a housing pot with Pot bottom and pot jacket and has a piston axially displaceable in the housing pot. There is a fluid-filled coupler gap between the piston and the bottom of the pot.
  • a first membrane made of steel is arranged, which defines a fluid-filled expansion chamber with the bottom of the pot. The first membrane covers the bottom of the pot and is attached to the edge of the cup by welding.
  • the compensation chamber is flow-connected to the coupler gap via a throttle element arranged in the bottom of the pot.
  • Pot bottom facing away from the end of the housing pot an existing between pot shell and piston annular gap.
  • the annular membrane is fixed with its outer edge of the membrane on the pot shell and with its inner edge of the membrane on the piston by welding.
  • a pressure distribution disc is inserted, which rests with a central elevation at the central region of the first membrane. Disclosure of the invention
  • the hydraulic coupler according to the invention with the features of claim 1 has the advantage that the wall thickness of the membrane can be kept small and thus a low stiffness of the membrane can be obtained by the additional axial spring force while maintaining a required in the valve installation state of the coupler Kopplerkraft. Due to the design of the spring element as a spring clip and the spring element has only a low spring stiffness, so that the gain reduction of the coupler obtained with the wall thickness reduction is not canceled. Overall, the overall stiffness of the coupler is kept advantageously low, so that the coupler clearly fulfills its task of compensating temperature-induced, different changes in length of two components with different thermal expansion coefficients, between which it is axially clamped. In addition, compared to a designed as a helical compression spring spring element is an essential
  • the spring clip on the pot sheath cross-spring shank and a spring leg interconnecting spring bridge, which rests with a central region on the membrane.
  • the determination of the spring clip is made by means of the spring legs, which are connected cohesively at their remote from the spring bridge leg ends with the pot jacket.
  • the spring bridge is concave, so that the central support area is realized in a simple manner.
  • the desired axial force acting on the membrane can be set very precisely prior to the cohesive fastening of the spring legs to the pot jacket by more or less axial sliding of the spring legs onto the housing pot.
  • the spring clip on two spring bridge to the diametrical spring legs, and spring legs and spring bridge are made in one piece from a spring band by punching or bending, so that the spring clip is a cost to be manufactured component.
  • the spring band in the spring bridge in turns, wherein advantageously the Wnditch are shaped so that the spring bridge is an S-shape with a straight central leg and two at each end of the middle leg continuing, curved outer legs has and the longitudinal axis of the middle
  • the spring band is made of high-strength spring steel, as it is for example also used for the membrane.
  • FIG. 1 shows a longitudinal section of a fuel injection valve with a hydraulic coupler
  • FIG. 2 is an enlarged view of section II in FIG. 1
  • FIG. 3 is a plan view of a spring clip of the hydraulic coupler in direction III in FIG. 2
  • the fuel injection valve shown in longitudinal section in Figure 1 as an exemplary embodiment of a general valve for metering a flowing medi- order, in particular a fluid, has a hollow cylindrical valve housing 1 1, one end of which is completed by a an injection or valve opening 13 having nozzle or valve body 12.
  • the valve opening 13 is controlled by an outwardly opening valve member 14, which is designed as a valve needle with a closing head, ie closed or released.
  • Valve member is actuated by an actuator 16 against the return force of the valve member 14 and the valve body 12 is supported return spring 15, wherein the valve member 14 releases the valve opening 13 via its closing head due to an applied voltage to the actuator 16.
  • the actuator 16 has an electrically controllable piezo module 19, also called a piezo stack, which is clamped by means of a hollow body 21 designed as a spring between a closure plate 18 and a closure body 20.
  • the actuator 16 engages via a gimbal bearing 17 on the valve member 14, wherein the gimbal bearing 17 is formed between the Schretekopffernen end of the valve needle of the valve member 14 and the end plate 18 of the actuator 16.
  • connection piece 22 is provided with a fluid connection 23 and an electrical connection plug 24.
  • connection plug 24 an electrical connection to the piezo module 20 of the actuator 16 is produced by means of an actuator-side contact member 25 and a housing-side contact member 26. Electrically conductive parts of the two contact members 25, 26 contact each other and are welded together at the contact points. Alternatively, the contacting parts of both contact members 25, 26 may be made integral with each other.
  • the hydraulic coupler 30, shown enlarged in longitudinal section in FIG. 2, has a housing pot 31 with a pot bottom 311 and a pot jacket 312 and a piston 33 guided axially displaceably in the housing pot 31.
  • the housing pot 31 is formed in a connection piece 22, blind hole-like recess
  • the cardan see storage is indicated in Figure 2 with 32.
  • the piston 33 is fixedly connected to the actuator 16, for which purpose in the piston 33, a central centering pin 34 with a projecting from the piston 33, hollow bolt head 341 firmly inserted, z. B. pressed, and the end body 20 of the actuator 16 is provided with an axially projecting pin 201, which reduced with a diameter
  • a fluid e.g. Oil, filled coupler gap 35 is present, and on the side facing away from the piston 33 outside of the housing pot 31, a thin first membrane 36 made of steel, which limits a flow-connected to the coupler gap 35 compensation chamber 37 on the outside of the housing pot 31.
  • the membrane 36 spans the pot bottom 31 1 and is fastened with its membrane edge to the pot jacket 312, e.g. cohesively connected to the pot jacket 312.
  • the material bond is symbolized in Figure 2 by a weld 39.
  • the first diaphragm 36 which is optimized in its design for a defined pressure generation in the compensation chamber 37, has a central, convex elevation 361 and a concave annular recess 362 concentrically surrounding it.
  • the membrane 36 facing bottom surface of the pot bottom 31 1 is adapted to the membrane shape.
  • a spring element 40 acts with an axially directed spring force on the membrane 36, so that an additional pressure in the fluid-filled compensation chamber
  • the likewise consisting of steel second membrane 41 is for this purpose annular and connected at its outer edge of the membrane with the pot jacket 312 and at its inner edge of the membrane with the piston 33 each cohesively.
  • the material connection at the inner edge of the membrane can also be made to the centering pin 34 pressed into the piston 33.
  • the cohesive connections are indicated in Figure 2 by welds 43 and 44.
  • the flow connection between the coupler gap 35 and the compensation chamber 37 is produced by at least one radial bore 38 in the pot jacket 312.
  • two diametrically arranged radial bores 38 are present, each in the sealed from the first diaphragm 36 compensation chamber 37 on the outside of the housing pot 31st and open in the annular gap 42 sealed by the second membrane 41 between the piston 33 and the cup jacket 312 of the housing pot 31.
  • the annular gap 42 acts as a throttle for the fluid flowing between the coupler gap 35 and the compensation chamber 37.
  • the spring element 40 is designed as a spring clip 45 which is fixed on the housing pot 31 and rests against the diaphragm 36 with axial prestressing.
  • the spring clip 45 has a plurality of, here two diametrically arranged spring legs 46, 47 and a spring leg 46, 47 interconnecting de spring bridge 48.
  • the spring legs 46, 47 engage over the membrane area lying against the pot jacket 312 and are firmly bonded to the pot jacket 312 with their leg ends facing away from the spring bridge 48.
  • the material bond is again indicated in FIG. 2 by a weld seam 49.
  • the spring bridge 48 spans the membrane area covering the pot bottom 31 1 and presses against the first membrane 36.
  • the spring bridge 48 is concavely arched for this purpose, thus has a protruding from the bridge edge in the space between the two spring legs 46, 47 concavity, wherein the concave curvature of the spring bridge 48 has a central region 484, which conformed to the convex elevation 361 of the membrane 36 is.
  • Spring bridge 48 and spring legs 46, 47 are produced in one piece from a spring band as a stamped and bent part, high-strength spring steel being used as band material. In the region of the spring bridge 48, the spring band runs in turns ( Figure 3).
  • the windings are shaped so that the spring bridge 48 S-shape with a straight central leg 481 and two, at one end of the middle leg 481 integrally adjoining, bent outer legs 482 and 483 and the axis of the central leg 481 and the axes the two spring legs 46, 47 lie in a plane which extends at right angles to the plane of the spring bridge 48.
  • the form-adapted central area 484 of the concave curvature of the spring bridge 48 resting on the convex elevation 361 of the first diaphragm 36 is on the middle one
  • Leg 481 is formed, and of the outer legs 482 and 483, the spring legs 46 and 47 are bent at right angles.
  • the spring legs 46,48 are axially pushed so far on the housing pot 31 that the spring bridge 48 presses with the desired bias on the first diaphragm 36.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Actuator (AREA)

Abstract

A hydraulic coupling, in particular for fuel injection valves, is specified, which hydraulic coupling has a housing pot (31) with pot bottom (311) and pot shell (312), a piston (33) which is guided axially displaceably in the housing pot (31), a fluid-filled coupling gap (35) which is provided between the piston (33) and the pot bottom (311), a diaphragm (36) which is arranged on that outer side of the housing pot (31) which faces away from the piston (33), a compensation chamber (37) which is delimited by the diaphragm (36) and is flow-connected to the coupling gap (35), and a spring element (40) which acts on the diaphragm (36) with an axially directed spring force. In order to achieve a low overall stiffness of the hydraulic coupling at the required predefined coupling force, the spring element (40) is configured as a spring clip (45) which is fixed on the housing pot (31) and bears with axial prestress against the diaphragm (36) in the region of the pot bottom (311).

Description

Beschreibung  description
Titel title
Hydraulischer Koppler Stand der Technik  Hydraulic coupler prior art
Die Erfindung geht aus von einem hydraulischen Koppler, insbesondere für Kraftstoffeinspritzventile, nach dem Oberbegriff des Anspruchs 1. Ein bekanntes Kraftstoffeinspritzventil (DE 10 2004 002 134 A1) weist einen zwischen einer Ventilnadel und einem piezoelektrischen Aktor axial eingespannten hydraulischen Koppler auf, der einen Gehäusetopf mit Topfboden und Topfmantel und einen im Gehäusetopf axial verschieblichen Kolben aufweist. Zwischen dem Kolben und dem Topfboden ist ein fluidgefüllter Kopplerspalt vorhanden. Auf der vom Kolben abgewandten Außenseite des Topfbodens ist eine erste Membran aus Stahl angeordnet, die mit dem Topfboden einen fluidgefüllten Ausgleichsraum begrenzt. Die erste Membran überdeckt dabei den Topfboden und ist randseitig am Topfmantel durch Schweißen befestigt. Der Ausgleichsraum ist über ein im Topfboden angeordnetes Drosselelement mit dem Kopplerspalt strömungsverbunden. Eine zweite Membran aus Stahl überdeckt an der vomThe invention is based on a hydraulic coupler, in particular for fuel injection valves, according to the preamble of claim 1. A known fuel injection valve (DE 10 2004 002 134 A1) has a between a valve needle and a piezoelectric actuator axially clamped hydraulic coupler having a housing pot with Pot bottom and pot jacket and has a piston axially displaceable in the housing pot. There is a fluid-filled coupler gap between the piston and the bottom of the pot. On the side facing away from the piston outside of the pot bottom, a first membrane made of steel is arranged, which defines a fluid-filled expansion chamber with the bottom of the pot. The first membrane covers the bottom of the pot and is attached to the edge of the cup by welding. The compensation chamber is flow-connected to the coupler gap via a throttle element arranged in the bottom of the pot. A second membrane of steel covered at the of
Topfboden abgewandten Stirnseite des Gehäusetopfes einen zwischen Topfmantel und Kolben vorhandenen Ringspalt. Die ringförmige Membran ist mit ihrem äußeren Membranrand am Topfmantel und mit ihrem inneren Membranrand am Kolben durch Schweißen festgelegt. Zur Erzeugung eines Überdrucks im Ausgleichsraum wirkt eine Schraubendruckfeder, die sich im Ventilgehäuse abstützt, mit axial gerichteter Federkraft auf die erste Membran, wobei zwischen Schraubendruckfeder und erster Membran eine Druckverteilungsscheibe eingelegt ist, die mit einer mittleren Erhebung an dem zentralen Bereich der ersten Membran anliegt. Offenbarung der Erfindung Pot bottom facing away from the end of the housing pot an existing between pot shell and piston annular gap. The annular membrane is fixed with its outer edge of the membrane on the pot shell and with its inner edge of the membrane on the piston by welding. To generate an overpressure in the expansion chamber acts a helical compression spring, which is supported in the valve housing, with axially directed spring force on the first membrane, between helical compression spring and the first membrane, a pressure distribution disc is inserted, which rests with a central elevation at the central region of the first membrane. Disclosure of the invention
Der erfindungsgemäße hydraulische Koppler mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass durch die zusätzliche axiale Federkraft bei Einhaltung ei- ner im Ventileinbauzustand des Kopplers geforderten Kopplerkraft die Wandstärke der Membran klein gehalten und damit eine geringe Steifigkeit der Membran gewonnen werden kann. Durch die Ausbildung des Federelements als Federbügel hat auch das Federelement eine nur geringe Federsteifigkeit, so dass die mit der Wandstärkenreduzierung gewonnene Steifigkeitsreduzierung des Kopplers nicht aufgehoben wird. Insgesamt wird die Gesamtsteifigkeit des Kopplers vorteilhaft niedrig gehalten, so dass der Koppler seine Aufgabe des Ausgleichs temperaturbedingter, unterschiedlicher Längenveränderungen zweier Bauteilen mit unterschiedlichen Wärmeausdehnungskoeffizienten, zwischen denen er axial eingespannt ist, deutlich toleranzenger erfüllt. Darüber hinaus wird gegenüber ei- nem als Schraubendruckfeder ausgebildeten Federelement ein wesentlicherThe hydraulic coupler according to the invention with the features of claim 1 has the advantage that the wall thickness of the membrane can be kept small and thus a low stiffness of the membrane can be obtained by the additional axial spring force while maintaining a required in the valve installation state of the coupler Kopplerkraft. Due to the design of the spring element as a spring clip and the spring element has only a low spring stiffness, so that the gain reduction of the coupler obtained with the wall thickness reduction is not canceled. Overall, the overall stiffness of the coupler is kept advantageously low, so that the coupler clearly fulfills its task of compensating temperature-induced, different changes in length of two components with different thermal expansion coefficients, between which it is axially clamped. In addition, compared to a designed as a helical compression spring spring element is an essential
Montagevorteil erzielt, da der Koppler nunmehr eine Komplettbaueinheit bildet und z.B. in ein Kraftstoffeinspritzventil ohne gesonderte Einzelmontage des Federelements eingebaut werden kann. Zudem kann die auf die Membran wirkende Federkraft vor dem Einbau des Kopplers eingestellt werden. Assembly advantage achieved since the coupler now forms a complete assembly and e.g. can be installed in a fuel injection valve without separate individual assembly of the spring element. In addition, the spring force acting on the membrane can be adjusted before installing the coupler.
Durch die in den weiten Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen hydraulischen Kopplers möglich. Gemäß einer vorteilhaften Ausführungsform der Erfindung weist der Federbügel den Topfmantel übergreifende Federschenkel und eine die Federschenkel miteinander verbindende Federbrücke auf, die mit einem zentralen Bereich auf der Membran aufliegt. Die Festlegung des Federbügels ist mittels der Federschenkel vorgenommen, die an ihren von der Federbrücke abgekehrten Schenkelenden mit dem Topfmantel stoffschlüssig verbunden sind. Die Federbrücke ist konkav gewölbt, so dass in einfacher Weise der zentrale Auflagebereich realisiert ist. Durch diese konstruktive Gestaltung des Federbügels lässt sich durch mehr oder weniger weites axiales Aufschieben der Federschenkel auf den Gehäusetopf die gewünschte, auf die Membran wirkende Axialkraft vor dem stoffschlüssigen Fest- legen der Federschenkel auf den Topfmantel sehr genau einstellen. Gemäß einer vorteilhaften Ausführungsform der Erfindung weist der Federbügel zwei zur Federbrücke diametrale Federschenkel auf, und Federschenkel und Federbrücke sind einstückig aus einem Federband durch Stanzen oder Biegen hergestellt, so dass der Federbügel ein kostengünstig zu fertigendes Bauteil ist. The measures listed in the broad claims advantageous refinements and improvements of the claim 1 hydraulic coupler are possible. According to an advantageous embodiment of the invention, the spring clip on the pot sheath cross-spring shank and a spring leg interconnecting spring bridge, which rests with a central region on the membrane. The determination of the spring clip is made by means of the spring legs, which are connected cohesively at their remote from the spring bridge leg ends with the pot jacket. The spring bridge is concave, so that the central support area is realized in a simple manner. As a result of this constructive design of the spring clip, the desired axial force acting on the membrane can be set very precisely prior to the cohesive fastening of the spring legs to the pot jacket by more or less axial sliding of the spring legs onto the housing pot. According to an advantageous embodiment of the invention, the spring clip on two spring bridge to the diametrical spring legs, and spring legs and spring bridge are made in one piece from a spring band by punching or bending, so that the spring clip is a cost to be manufactured component.
Gemäß einer vorteilhaften Ausführungsform der Erfindung verläuft das Federband im Bereich der Federbrücke in Windungen, wobei vorteilhaft die Wndungen so geformt sind, dass die Federbrücke eine S-Form mit einem geraden mittleren Schenkel und zwei an jedem Ende des mittleren Schenkels sich fortsetzenden, gebogenen äußeren Schenkeln aufweist und die Längsachse des mittlerenAccording to an advantageous embodiment of the invention, the spring band in the spring bridge in turns, wherein advantageously the Wndungen are shaped so that the spring bridge is an S-shape with a straight central leg and two at each end of the middle leg continuing, curved outer legs has and the longitudinal axis of the middle
Schenkels und die Längsachsen der beiden Federschenkel in einer zur Federbrücke sich rechtwinklig erstreckenden Ebene liegen. Durch diese konstruktive Gestaltung der Federbrücke lässt sich die von dem Federbügel auf die Membran einwirkende axiale Federkraft sehr genau mit geringen Toleranzen justieren. Leg and the longitudinal axes of the two spring legs lie in a plane perpendicular to the spring bridge extending plane. Through this constructive design of the spring bridge, the axial spring force acting on the membrane from the spring clip can be adjusted very precisely with small tolerances.
Gemäß einer vorteilhaften Ausführungsform der Erfindung ist das Federband aus hochfestem Federstahl hergestellt, wie er beispielsweise auch für die Membran verwendet wird. Kurze Beschreibung der Zeichnungen According to an advantageous embodiment of the invention, the spring band is made of high-strength spring steel, as it is for example also used for the membrane. Brief description of the drawings
Die Erfindung ist anhand eines in den Zeichnungen dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Es zeigen: Figur 1 einen Längsschnitt eines Kraftstoffeinspritzventils mit einem hydraulischen Koppler, The invention is explained in more detail in the following description with reference to an embodiment shown in the drawings. 1 shows a longitudinal section of a fuel injection valve with a hydraulic coupler,
Figur 2 eine vergrößerte Darstellung des Ausschnitts II in Figur 1 , Figur 3 eine Draufsicht eines Federbügels des hydraulischen Kopplers in Richtung III in Figur 2, 2 is an enlarged view of section II in FIG. 1, FIG. 3 is a plan view of a spring clip of the hydraulic coupler in direction III in FIG. 2,
Figur 4 einen Schnitt längs der Linie IV - IV in Figur 3. 4 shows a section along the line IV - IV in Figure 3.
Das in Figur 1 im Längsschnitt dargestellte Kraftstoffeinspritzventil als Ausführungsbeispiel für ein allgemeines Ventil zum Zumessen eines strömenden Medi- ums, insbesondere eines Fluids, weist ein hohlzylindrisches Ventilgehäuse 1 1 auf, dessen eines Stirnende von einem eine Abspritz- oder Ventilöffnung 13 aufweisenden Düsen- oder Ventilkörper 12 abgeschlossen ist. Die Ventilöffnung 13 wird von einem nach außen öffnenden Ventilglied 14, das als Ventilnadel mit Schließkopf ausgebildet ist, gesteuert, also geschlossen oder freigegeben. DasThe fuel injection valve shown in longitudinal section in Figure 1 as an exemplary embodiment of a general valve for metering a flowing medi- order, in particular a fluid, has a hollow cylindrical valve housing 1 1, one end of which is completed by a an injection or valve opening 13 having nozzle or valve body 12. The valve opening 13 is controlled by an outwardly opening valve member 14, which is designed as a valve needle with a closing head, ie closed or released. The
Ventilglied wird von einem Aktor 16 gegen die Rückstell kraft einer an dem Ventilglied 14 und am Ventilkörper 12 sich abstützenden Rückstellfeder 15 betätigt, wobei infolge einer an den Aktor 16 angelegten elektrische Spannung das Ventilglied 14 über seinen Schließkopf die Ventilöffnung 13 freigibt. Der Aktor 16 be- sitzt einen elektrisch ansteuerbaren Piezomodul 19, auch Piezostack genannt, der mittels eines als Feder ausgebildeten Hohlkörpers 21 zwischen einer Abschlussplatte 18 und einem Abschlusskörper 20 eingespannt ist. Der Aktor 16 greift dabei über ein kardanisches Lager 17 an dem Ventilglied 14 an, wobei das kardanische Lager 17 zwischen dem schließkopffernen Ende der Ventilnadel des Ventilglieds 14 und der Abschlussplatte 18 des Aktors 16 ausgebildet ist. Valve member is actuated by an actuator 16 against the return force of the valve member 14 and the valve body 12 is supported return spring 15, wherein the valve member 14 releases the valve opening 13 via its closing head due to an applied voltage to the actuator 16. The actuator 16 has an electrically controllable piezo module 19, also called a piezo stack, which is clamped by means of a hollow body 21 designed as a spring between a closure plate 18 and a closure body 20. The actuator 16 engages via a gimbal bearing 17 on the valve member 14, wherein the gimbal bearing 17 is formed between the Schließkopffernen end of the valve needle of the valve member 14 and the end plate 18 of the actuator 16.
In das vom Ventilkörper 12 abgekehrte Ende des Ventilgehäuses 11 ist ein Anschlussstück 22 fest eingesetzt. Das Anschlussstück 22 ist mit einem Flui- danschluss 23 und einem elektrischen Anschlussstecker 24 versehen. Vom An- schlussstecker 24 ist mittels eines aktorseitigen Kontaktglieds 25 und eines ge- häuseseitigen Kontaktglieds 26 eine elektrische Verbindung zum Piezomodul 20 des Aktors 16 hergestellt. Elektrisch leitende Teile der beiden Kontaktglieder 25, 26 kontaktieren einander und sind an den Kontaktstellen miteinander verschweißt. Alternativ können die einander kontaktierenden Teile beider Kontakt- glieder 25, 26 auch miteinander einstückig ausgeführt werden. Der VentilkörperIn the remote from the valve body 12 end of the valve housing 11, a connector 22 is firmly inserted. The connection piece 22 is provided with a fluid connection 23 and an electrical connection plug 24. From the connection plug 24, an electrical connection to the piezo module 20 of the actuator 16 is produced by means of an actuator-side contact member 25 and a housing-side contact member 26. Electrically conductive parts of the two contact members 25, 26 contact each other and are welded together at the contact points. Alternatively, the contacting parts of both contact members 25, 26 may be made integral with each other. The valve body
12 und das Anschlussstück 22 sind über ein Rohr 27 fest miteinander verbunden, wobei die Rückstellfeder 15, der Aktor 16 und ein hydraulischer Koppler 30 im Rohr 27 aufgenommen sind. Der Aktor 16 stützt sich über den hydraulischen Koppler 30 am Ventilgehäuse 1 1 , genauer gesagt an dem fest mit dem Ventilge- häuse 11 verbundenen Anschlussstück 22, ab. 12 and the connector 22 are fixedly connected to each other via a tube 27, wherein the return spring 15, the actuator 16 and a hydraulic coupler 30 are received in the tube 27. The actuator 16 is supported via the hydraulic coupler 30 on the valve housing 1 1, more precisely on the fixedly connected to the valve housing 11 connecting piece 22 from.
Der in Figur 2 vergrößert im Längsschnitt dargestellte hydraulische Koppler 30 weist einen Gehäusetopf 31 mit Topfboden 311 und Topfmantel 312 sowie einen im Gehäusetopf 31 axial verschieblich geführten Kolben 33 auf. Der Gehäusetopf 31 ist in einer im Anschlussstück 22 ausgebildeten, sacklochartigen AusnehmungThe hydraulic coupler 30, shown enlarged in longitudinal section in FIG. 2, has a housing pot 31 with a pot bottom 311 and a pot jacket 312 and a piston 33 guided axially displaceably in the housing pot 31. The housing pot 31 is formed in a connection piece 22, blind hole-like recess
29 aufgenommen und am Anschlussstück 22 kardanisch gelagert. Die kardani- sehe Lagerung ist in Figur 2 mit 32 gekennzeichnet. Der Kolben 33 ist fest mit dem Aktor 16 verbunden, wozu in den Kolben 33 ein zentraler Zentrierbolzen 34 mit einem vom Kolben 33 abstehenden, hohlen Bolzenkopf 341 fest eingesetzt, z. B. eingepresst, und der Abschlusskörper 20 des Aktors 16 mit einem axial ab- stehenden Zapfen 201 versehen ist, der mit einem im Durchmesser reduzierten29 recorded and gimbals mounted on the connector 22. The cardan see storage is indicated in Figure 2 with 32. The piston 33 is fixedly connected to the actuator 16, for which purpose in the piston 33, a central centering pin 34 with a projecting from the piston 33, hollow bolt head 341 firmly inserted, z. B. pressed, and the end body 20 of the actuator 16 is provided with an axially projecting pin 201, which reduced with a diameter
Endabschnitt in den hohlen Bolzenkopf 341 eingepresst ist. Zwischen dem Kolben 33 und dem Topfboden 31 1 des Gehäusetopfs 31 ist ein mit Fluid, z.B. Öl, gefüllter Kopplerspalt 35 vorhanden, und auf der vom Kolben 33 abgekehrten Außenseite des Gehäusetopfes 31 ist eine dünne erste Membran 36 aus Stahl angeordnet, die einen mit dem Kopplerspalt 35 strömungsverbundenen Ausgleichsraum 37 auf der Außenseite des Gehäusetopfes 31 begrenzt. Die Membran 36 überspannt hierzu den Topfboden 31 1 und ist mit ihrem Membranrand am Topfmantel 312 befestigt, z.B. stoffschlüssig mit dem Topfmantel 312 verbunden. Der Stoffschluss ist in Figur 2 durch eine Schweißnaht 39 symbolisiert. Die in ih- rer Formgestaltung für eine definierte Druckerzeugung im Ausgleichsraum 37 optimierte erste Membran 36 weist eine zentrale, konvexe Erhebung 361 und eine diese konzentrisch umschließende, konkave Ringmulde 362 auf. Die der Membran 36 zugewandte Bodenfläche des Topfbodens 31 1 ist an die Membranform angepasst. Ein Federelement 40 wirkt mit einer axial gerichteten Federkraft auf die Membran 36, so dass ein zusätzlicher Druck im fluidgefüllten AusgleichsraumEnd portion is pressed into the hollow bolt head 341. Between the piston 33 and the pot bottom 31 1 of the housing pot 31 is provided with a fluid, e.g. Oil, filled coupler gap 35 is present, and on the side facing away from the piston 33 outside of the housing pot 31, a thin first membrane 36 made of steel, which limits a flow-connected to the coupler gap 35 compensation chamber 37 on the outside of the housing pot 31. For this purpose, the membrane 36 spans the pot bottom 31 1 and is fastened with its membrane edge to the pot jacket 312, e.g. cohesively connected to the pot jacket 312. The material bond is symbolized in Figure 2 by a weld 39. The first diaphragm 36, which is optimized in its design for a defined pressure generation in the compensation chamber 37, has a central, convex elevation 361 and a concave annular recess 362 concentrically surrounding it. The membrane 36 facing bottom surface of the pot bottom 31 1 is adapted to the membrane shape. A spring element 40 acts with an axially directed spring force on the membrane 36, so that an additional pressure in the fluid-filled compensation chamber
37 aufgebaut wird. 37 is built.
Eine an der vom Topfboden 311 abgewandten Stirnseite des Gehäusetopfes 31 angeordnete, dünne zweite Membran 41 dichtet einen zwischen dem Kolben 33 und dem Topfmantel 312 des Gehäusetopfes 31 vorhandenen Ringspalt 42 flu- iddicht ab. Die ebenfalls aus Stahl bestehende zweite Membran 41 ist hierzu ringförmig ausgebildet und an ihrem äußeren Membranrand mit dem Topfmantel 312 und an ihrem inneren Membranrand mit dem Kolben 33 jeweils stoffschlüssig verbunden. Alternativ kann der Stoffschluss am inneren Membranrand auch zu dem in den Kolben 33 eingepressten Zentrierbolzen 34 hergestellt sein. Die stoffschlüssigen Verbindungen sind in Figur 2 durch Schweißnähte 43 und 44 angedeutet. Die Strömungsverbindung zwischen Kopplerspalt 35 und Ausgleichsraum 37 ist durch mindestens eine Radialbohrung 38 im Topfmantel 312 hergestellt. Im Ausführungsbeispiel der Figur 2 sind zwei diametral angeordnete Radialbohrungen 38 vorhanden, die jeweils in dem von der ersten Membran 36 abgedichteten Ausgleichsraum 37 auf der Außenseite des Gehäusetopfes 31 und in dem von der zweiten Membran 41 abgedichteten Ringspalt 42 zwischen dem Kolben 33 und dem Topfmantel 312 des Gehäusetopfes 31 münden. Der Ringspalt 42 wirkt als Drossel für das zwischen Kopplerspalt 35 und Ausgleichsraum 37 srömende Fluid. A thin second membrane 41 arranged at the end face of the housing pot 31 facing away from the bottom of the pot 311 seals a ring gap 42 between the piston 33 and the cup jacket 312 of the housing pot 31 in a fluid-tight manner. The likewise consisting of steel second membrane 41 is for this purpose annular and connected at its outer edge of the membrane with the pot jacket 312 and at its inner edge of the membrane with the piston 33 each cohesively. Alternatively, the material connection at the inner edge of the membrane can also be made to the centering pin 34 pressed into the piston 33. The cohesive connections are indicated in Figure 2 by welds 43 and 44. The flow connection between the coupler gap 35 and the compensation chamber 37 is produced by at least one radial bore 38 in the pot jacket 312. In the embodiment of Figure 2, two diametrically arranged radial bores 38 are present, each in the sealed from the first diaphragm 36 compensation chamber 37 on the outside of the housing pot 31st and open in the annular gap 42 sealed by the second membrane 41 between the piston 33 and the cup jacket 312 of the housing pot 31. The annular gap 42 acts as a throttle for the fluid flowing between the coupler gap 35 and the compensation chamber 37.
Das Federelement 40 ist als Federbügel 45 ausgebildet, der auf dem Gehäusetopf 31 festgelegt ist und mit axialer Vorspannung an der Membran 36 anliegt. Der Federbügel 45 weist mehrere, hier insgesamt zwei diametral angeordnete Federschenkel 46, 47 und eine die Federschenkel 46, 47 miteinander verbinden- de Federbrücke 48 auf. Die Federschenkel 46, 47 übergreifen den am Topfmantel 312 anliegenden Membranbereich und sind mit ihren von der Federbrücke 48 abgekehrten Schenkelenden stoffschlüssig auf dem Topfmantel 312 festgelegt. Der Stoffschluss ist in Figur 2 wiederum durch eine Schweißnaht 49 angedeutet. Die Federbrücke 48 überspannt den den Topfboden 31 1 überziehenden Memb- ranbereich und presst sich an die erste Membran 36 an. Die Federbrücke 48 ist hierzu konkav gewölbt, weist also eine vom Brückenrand in den Zwischenraum zwischen den beiden Federschenkeln 46, 47 hineinragende Einwölbung auf, wobei die konkave Einwölbung der Federbrücke 48 einen zentralen Bereich 484 besitzt, der an die konvexe Erhebung 361 der Membran 36 formangepasst ist. Fe- derbrücke 48 und Federschenkel 46, 47 sind einstückig aus einem Federband als Stanz-Biegeteil hergestellt, wobei als Bandmaterial hochfester Federstahl verwendet wird. Im Bereich der Federbrücke 48 verläuft das Federband in Windungen (Figur 3). Die Windungen sind so geformt, dass die Federbrücke 48 S- Form mit einem geraden mittleren Schenkel 481 und zwei sich an jeweils einem Ende des mittleren Schenkels 481 einstückig anschließenden, gebogenen äußeren Schenkel 482 und 483 aufweist und die Achse des mittleren Schenkels 481 und die Achsen der beiden Federschenkel 46, 47 in einer Ebene liegen, die sich rechtwinklig zur Ebene der Federbrücke 48 erstreckt. Der auf der konvexen Erhebung 361 der ersten Membran 36 aufliegende, formangepasste zentrale Be- reich 484 der konkaven Einwölbung der Federbrücke 48 ist am mittlerenThe spring element 40 is designed as a spring clip 45 which is fixed on the housing pot 31 and rests against the diaphragm 36 with axial prestressing. The spring clip 45 has a plurality of, here two diametrically arranged spring legs 46, 47 and a spring leg 46, 47 interconnecting de spring bridge 48. The spring legs 46, 47 engage over the membrane area lying against the pot jacket 312 and are firmly bonded to the pot jacket 312 with their leg ends facing away from the spring bridge 48. The material bond is again indicated in FIG. 2 by a weld seam 49. The spring bridge 48 spans the membrane area covering the pot bottom 31 1 and presses against the first membrane 36. The spring bridge 48 is concavely arched for this purpose, thus has a protruding from the bridge edge in the space between the two spring legs 46, 47 concavity, wherein the concave curvature of the spring bridge 48 has a central region 484, which conformed to the convex elevation 361 of the membrane 36 is. Spring bridge 48 and spring legs 46, 47 are produced in one piece from a spring band as a stamped and bent part, high-strength spring steel being used as band material. In the region of the spring bridge 48, the spring band runs in turns (Figure 3). The windings are shaped so that the spring bridge 48 S-shape with a straight central leg 481 and two, at one end of the middle leg 481 integrally adjoining, bent outer legs 482 and 483 and the axis of the central leg 481 and the axes the two spring legs 46, 47 lie in a plane which extends at right angles to the plane of the spring bridge 48. The form-adapted central area 484 of the concave curvature of the spring bridge 48 resting on the convex elevation 361 of the first diaphragm 36 is on the middle one
Schenkel 481 ausgebildet, und von den äußeren Schenkeln 482 und 483 sind die Federschenkel 46 und 47 rechtwinklig abgebogen. Die Federschenkel 46,48 sind axial soweit auf den Gehäusetopf 31 aufgeschoben, dass die Federbrücke 48 mit der gewünschten Vorspannung auf die erste Membran 36 drückt. Leg 481 is formed, and of the outer legs 482 and 483, the spring legs 46 and 47 are bent at right angles. The spring legs 46,48 are axially pushed so far on the housing pot 31 that the spring bridge 48 presses with the desired bias on the first diaphragm 36.

Claims

Hydraulischer Koppler, insbesondere für Kraftstoffeinspritzventile, mit einem Topfboden (311) und Topfmantel (312) aufweisenden Gehäusetopf (31), mit einem im Gehäusetopf (31) axial verschieblich geführten Kolben (33) , mit einem zwischen Kolben (33) und Topfboden (31 1) vorhandenen, fluidgefüll- ten Kopplerspalt (35), mit einer auf der vom Kolben (33) abgekehrten Außenseite des Gehäusetopfes (31) angeordneten Membran (36), die einen mit dem Kopplerspalt (35) strömungsverbundenen Ausgleichsraum (37) begrenzt, und mit einem auf die Membran (36) mit axial gerichteter Federkraft wirkenden Federelement (40), dadurch gekennzeichnet, dass das Federelement (40) als ein am Gehäusetopf (31) festgelegter Federbügel (45) ausgebildet ist, der im Bereich des Topfbodens (311) mit axialer Vorspannung an der Membran (36) anliegt.  Hydraulic coupler, in particular for fuel injection valves, with a pot bottom (311) and pot shell (312) having housing pot (31), with a housing pot (31) axially displaceably guided piston (33), with a between piston (33) and cup bottom (31 1) existing, fluid-filled coupler gap (35), with a on the side facing away from the piston (33) outside of the housing pot (31) arranged membrane (36) defining a with the coupler gap (35) flow-connected compensation chamber (37), and with a spring element (40) acting on the membrane (36) with an axially directed spring force, characterized in that the spring element (40) is designed as a spring clip (45) fixed to the housing pot (31), which is located in the region of the pot bottom (311). with axial prestress against the membrane (36).
Hydraulischer Koppler nach Anspruch 1 , dadurch gekennzeichnet, dass der Federbügel (45) den Topfmantel (312) übergreifende Federschenkel (46, 47) und eine die Federschenkel (46, 47) miteinander verbindende Federbrücke (48) aufweist, die mit einem zentralen Bereich an der Membran (36) anliegt. Hydraulic coupler according to claim 1, characterized in that the spring clip (45) has the pot jacket (312) cross-spring legs (46, 47) and a spring legs (46, 47) interconnecting spring bridge (48) which connects to a central region the membrane (36) rests.
Hydraulischer Koppler nach Anspruch 2, dadurch gekennzeichnet, dass die Federbrücke (48) konkav eingewölbt ist. Hydraulic coupler according to claim 2, characterized in that the spring bridge (48) is concave.
Hydraulischer Koppler nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Festlegung des Federbügels (35) mittels der Federschenkel (46, 47) am Topfmantel (312) vorgenommen ist. Hydraulic coupler according to claim 2 or 3, characterized in that the fixing of the spring clip (35) by means of the spring legs (46, 47) on the pot jacket (312) is made.
Hydraulischer Koppler nach Anspruch 4, dadurch gekennzeichnet, dass die von der Federbrücke (48) abgewandten Schenkelenden der Federschenkel (46, 47) mit dem Topfmantel (312) des Gehäusetopfes (31) stoffschlüssig verbunden sind. Hydraulischer Koppler nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass der Federbügel (45) zwei diametral angeordnete Federschenkel (46, 47) aufweist und Federschenkel (46, 47) und Federbrücke (48) einstückig aus einem Federband, vorzugsweise als Stanz-Biegeteil, hergestellt sind. Hydraulic coupler according to claim 4, characterized in that the spring bridge (48) facing away from the leg ends of the spring legs (46, 47) with the pot jacket (312) of the housing pot (31) are materially connected. Hydraulic coupler according to one of claims 2 to 5, characterized in that the spring clip (45) has two diametrically arranged spring legs (46, 47) and spring legs (46, 47) and spring bridge (48) in one piece from a spring band, preferably as a punching Bending part, are made.
Hydraulischer Koppler nach Anspruch 6, dadurch gekennzeichnet, dass das Federband im Bereich der Federbrücke (48) in Windungen verläuft. Hydraulic coupler according to claim 6, characterized in that the spring band in the region of the spring bridge (48) runs in turns.
Hydraulischer Koppler nach Anspruch 7, dadurch gekennzeichnet, dass die Windungen so geformt sind, dass die Federbrücke (48) S-Form mit einem geraden mittleren Schenkel (481) und zwei sich an diesen beidendig anschließenden, gebogenen äußeren Schenkeln (482, 483) aufweist, wobei die Längsachse des mittleren Schenkels (481) der Federbrücke (48) und die Längsachsen der beiden Federschenkel (46, 47) in einer zur Federbrücke (48) sich rechtwinklig erstreckenden Ebene liegen. Hydraulic coupler according to claim 7, characterized in that the windings are shaped so that the spring bridge (48) S-shape with a straight middle leg (481) and two adjoining these at both ends, curved outer legs (482, 483) , wherein the longitudinal axis of the middle leg (481) of the spring bridge (48) and the longitudinal axes of the two spring legs (46, 47) lie in a plane perpendicular to the spring bridge (48) extending plane.
Hydraulischer Koppler nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, dass das Federband aus hochfestem Federstahl besteht. Hydraulic coupler according to one of claims 6 to 8, characterized in that the spring band consists of high-strength spring steel.
Hydraulischer Koppler nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Membran (36) den Topfboden (311) überspannt und mit ihrem Membranrand stoffschlüssig mit dem Topfmantel (312) verbunden ist. Hydraulic coupler according to one of claims 1 to 9, characterized in that the membrane (36) spans the pot bottom (311) and is integrally connected with its membrane edge to the pot jacket (312).
Hydraulischer Koppler nach Anspruch 10, dadurch gekennzeichnet, dass die Membran (36) eine zentrale, konvexe Erhebung (361 ) und eine die Erhebung (361 ) umschließende, konkave Ringmulde (362) aufweist und die der Membran (36) zugewandte Bodenfläche des Topfbodens (311) an die Membranform angepasst ist und dass die konkav eingewölbte Federbrücke (48) des Federbügels (45) mit einem an die konvexe Erhebung (361 ) der Membran (36) formangepassten, zentralen Bereich (484) auf der Membran (36) aufliegt. Hydraulic coupler according to claim 10, characterized in that the membrane (36) has a central, convex elevation (361) and a concave annular recess (362) enclosing the elevation (361) and the bottom surface of the pan bottom facing the membrane (36) ( 311) is adapted to the membrane shape and that the concave vaulted spring bridge (48) of the spring clip (45) with a to the convex elevation (361) of the membrane (36) form-fitting, central region (484) rests on the membrane (36).
Hydraulischer Koppler nach einem der Ansprüche 1 bis 1 1 , dadurch gekennzeichnet, dass zur Strömungsverbindung von Kopplerspalt (35) und Ausgleichsraum (37) im Topfmantel (312) des Gehäusetopfes (31) mindestens eine Radialbohrung (38) angeordnet ist, die einerseits zum Ausgleichsraum (37) und andererseits zu einem zwischen Kolben (33) und Topfmantel (312) des Gehäusetopfes (31) vorhandener Ringspalt (42) hin offen ist, und dass der Ringspalt (42) auf der vom Topfboden (31 1) abgewandten Stirnseite des Gehäusetopfes (31) von einer ringförmigen Membran (41) überdeckt ist, die mit ihrem äußeren Membranrand am Topfmantel (311) und mit ihrem inneren Membranrand am Kolben (33) jeweils fluiddicht festgelegt ist. Hydraulic coupler according to one of claims 1 to 1 1, characterized in that for the flow connection of the coupler gap (35) and compensation chamber (37) in the cup jacket (312) of the housing pot (31) at least a radial bore (38) is arranged, which on the one hand to the compensation chamber (37) and on the other hand to a between piston (33) and pot shell (312) of the housing pot (31) existing annular gap (42) is open, and that the annular gap (42) on the side facing away from the bottom of the pot (31 1) end of the housing pot (31) is covered by an annular membrane (41), which is fixed in each case fluid-tight with its outer edge of the membrane on Topfmantle (311) and with its inner edge of the membrane on the piston (33).
EP12770055.7A 2011-10-14 2012-09-25 Hydraulic coupling Active EP2766593B1 (en)

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RU2014119129A (en) 2015-12-10
IN2014CN02720A (en) 2015-07-03
CN103874848A (en) 2014-06-18
CN103874848B (en) 2016-10-26
EP2766593B1 (en) 2015-06-10
KR20140073525A (en) 2014-06-16
JP2014528548A (en) 2014-10-27
US9624886B2 (en) 2017-04-18
DE102011084512A1 (en) 2013-04-18
US20150048265A1 (en) 2015-02-19
WO2013053594A1 (en) 2013-04-18
RU2606731C2 (en) 2017-01-10
JP5916868B2 (en) 2016-05-11

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