EP2488731B1 - Volume accumulator - Google Patents

Volume accumulator Download PDF

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Publication number
EP2488731B1
EP2488731B1 EP20100781450 EP10781450A EP2488731B1 EP 2488731 B1 EP2488731 B1 EP 2488731B1 EP 20100781450 EP20100781450 EP 20100781450 EP 10781450 A EP10781450 A EP 10781450A EP 2488731 B1 EP2488731 B1 EP 2488731B1
Authority
EP
European Patent Office
Prior art keywords
guide housing
indentation
guide
spring element
camshaft
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
EP20100781450
Other languages
German (de)
French (fr)
Other versions
EP2488731A1 (en
Inventor
Eduard Golovatai-Schmidt
Mathias Boegershausen
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2488731A1 publication Critical patent/EP2488731A1/en
Application granted granted Critical
Publication of EP2488731B1 publication Critical patent/EP2488731B1/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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/21—Accumulator cushioning means using springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/405—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/60—Assembling or methods for making accumulators
    • F15B2201/605—Assembling or methods for making housings therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7792—Movable deflector or choke

Definitions

  • the invention relates to a volume accumulator with a guide housing and a separating element, wherein the separating element is displaceably mounted on an inner circumferential surface of the guide housing.
  • Volume accumulators are used, for example, in internal combustion engines to support the pressure medium supply of a hydraulic consumer, for example a camshaft adjuster or an electrohydraulic valve actuation device.
  • Camshaft adjusters are for example from the DE 195 29 277 A1 or the EP 0 806 550 A1 known.
  • a volume memory is for example in the DE 10 2007 041 552 A1 disclosed.
  • the volume accumulator has a hollow-cylindrical guide housing and a separating element received axially displaceably in the guide housing, in the illustrated embodiment a cup-shaped piston which divides the interior of the guide housing into a storage space and a complementary space.
  • the piston By pressurizing the piston, it is displaced against the force of a spring element in the direction of a stop, whereby the volume of the storage space increases at the expense of the volume of the complementary space.
  • the displacement of the piston is limited by the fact that an open end of a shell portion of the cup-shaped piston comes to rest on an annular, formed separately to the guide housing stop.
  • the annular stop abuts a radially extending wall at an axial end of the guide housing, at the same time the spring element is supported.
  • the invention has for its object to provide a volume storage, the production cost is to be reduced.
  • the object is achieved in that at least one indentation is formed on the guide housing, which projects into the guide housing, wherein the indentation in the direction of the separating element has an open end, which serves as a stop for the separating element.
  • the volume accumulator has a separating element, for example a piston, which is displaceably mounted within a guide housing and separates a storage space from a complementary space.
  • a separating element for example a piston
  • the latter is displaced within the guide housing in the direction of a stop which limits the displacement path of the separating element in that it comes into contact with the stop.
  • the stop secures the separator against unwanted leakage from the guide housing during its operation.
  • suitable spring strengths and spring lengths can be used and so the volume storage characteristics are designed appropriately.
  • the stopper is formed from the material of the guide housing.
  • a slot is provided in the example, hollow cylindrical guide housing, which runs along a non-self-contained line.
  • the slot extends at least partially in a plane perpendicular to the direction of displacement of the piston.
  • the slot can be introduced, for example, by punching or fine cutting in the guide housing.
  • In the area of the slot is on the guide housing provided a recess which projects into the interior of the guide housing.
  • an open end of the indentation created by the slot is opposite the piston and serves as a stop.
  • the open end is meant the area which was connected to the guide housing prior to the insertion of the slot.
  • the stop is on the one hand formed integrally with the guide housing, so that no additional components are needed.
  • the indentation can take a variety of forms. Conceivable, for example, embodiments in which a slot is introduced into the guide housing, which is arranged completely in a plane perpendicular to the direction of displacement of the piston. Subsequently, the indentation is introduced in the region of the slot in the guide housing.
  • the indentation is designed as a tab.
  • a deviating from a straight line slot is introduced into the guide housing, which forms a connected to the guide housing tab.
  • This can for example be triangular or square and optionally arched according to the shape of the guide housing and protrudes into the guide housing.
  • a spring element is arranged, which passes through the region of the recess, wherein the indentation has a guide portion for the spring element whose length in the direction of force of the spring element is greater than the distance between two turns of the spring element.
  • the guide portion provides a guide surface for the spring element, the the piston against the force of the pressure medium applied with a force.
  • the spring element may be formed, for example, as a helical or helical compression spring. It is ensured by the appropriate choice of the length of the guide portion that always one turn of the spring element is arranged in this area and thus the spring element is sufficiently guided so that the spring coils do not tilt on the stop of the tab.
  • the separating element can be designed, for example, as a cup-shaped piston with a bottom and a shell section adjoining it.
  • the guide housing and the piston without cutting are each made of a sheet metal blank, for example by means of a deep drawing process.
  • the jacket portion of the piston and the inner circumferential surface of the guide housing may be formed, for example, cylindrical or polygonal in cross-section.
  • the bottom of the piston serves as a pressure surface, which is acted upon by the inflowing pressure medium with a force, whereby the piston is displaced.
  • the lateral surface serves to support the piston in the guide housing, with the open end of the jacket section coming into contact with the stop when the volume reservoir is completely filled.
  • the sealing of the storage space relative to the complementary space via a closely tolerated clearance between the shell portion and the inner circumferential surface of the guide housing.
  • FIG. 1 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second camshaft adjuster 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslassgas scaffoldventile 10.
  • the Figures 2 and 3 show a camshaft adjuster 11 in longitudinal or in cross section.
  • a volume accumulator 15 which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 11.
  • the phaser 11 includes a drive element 14, an output element 16 and two side covers 17, 18 which are arranged on the axial side surfaces of the drive element 14.
  • the output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 19, extend from the outer cylindrical surface in the illustrated embodiment, five wings 20 in the radial direction outwardly.
  • five pressure chambers 22 are provided, wherein in each pressure chamber 22, a wing 20 protrudes.
  • the wings 20 are formed such that they rest against both the side covers 17, 18, and on the peripheral wall 21. Each wing 20 thus divides the respective pressure chamber 22 into two counteracting pressure chambers 23, 24th
  • a sprocket 12 is formed, via which by means of a chain drive, not shown, torque from the crankshaft 2 to the drive element 14 can be transmitted.
  • the output member 16 is rotatably connected by means of a central screw 13 with the camshaft 6,7.
  • the output element 16 is arranged rotatably in a defined Winkelbreich to the drive element 14.
  • the phase position of the drive element 14 to the output element 16 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied.
  • the phase position can be kept constant.
  • the camshaft 6, 7 has a plurality of openings 28, via which pressure medium conveyed by a pressure medium pump 37 passes into its interior.
  • a pressure medium path 29 formed on the one hand communicates with the openings 28 and on the other hand with a control valve 27 which serves to supply the camshaft adjuster 11 with pressure medium.
  • the control valve 27 is arranged in the interior of the central screw 13. By means of the control valve 27, pressure medium can be selectively directed to the first or second pressure chambers 23, 24 and discharged from the respective other pressure chambers 23, 24.
  • a pressure medium channel 30 is provided, which communicates on the one hand with the pressure medium path 29 and on the other hand with a cavity 31 of the hollow camshaft 6, 7.
  • the pressure medium channel 30 is formed as an axial bore, which passes through the threaded portion of the central screw 13.
  • the volume accumulator 15 is arranged in the cavity 31, the volume memory 15 comprises a guide housing 33, a separating element 34 and a force accumulator, which is designed in the illustrated embodiment as a spring element 35 in the form of a helical compression spring.
  • the guide housing 33 is non-positively connected to a wall 36 of the cavity 31. Also conceivable are embodiments in which the guide housing 33 is connected to the wall 36 in a material- or form-fitting manner.
  • the separating element 34 is arranged axially displaceable, wherein this is formed in the illustrated embodiment as a cup-shaped piston having a bottom 25 and a jacket portion 26.
  • the separating element 34 is mounted axially displaceably in the guide housing 33.
  • the outer lateral surface of the separating element 34 is adapted to the inner lateral surface of the guide housing 33 in such a way that the guide housing 33 is separated in a pressure medium-tight manner into a reservoir 45 axially in front of and a complementary space 46 behind the bottom 25 of the separating element 34.
  • the spring element 35 is supported on the one hand on a spring bearing 39 (FIG. FIG.
  • the spring element 35 acts on the separating element 34 with a force in the direction of the pressure medium channel 30.
  • the spring bearing 39 is formed as a radial indentation 47 of the guide housing 33.
  • a first slot 40 is inserted into the cylindrical guide housing 33, which extends in the circumferential direction of the guide housing 33.
  • the guide housing 33 is deformed radially inwardly in the region between the first slot 40 and the end remote from the camshaft.
  • the depth of the indentation 47 produced thereby is selected so that the spring element 35 bears against the open end of the spring bearing 39 even at maximum spring eccentricity, which has been separated from the guide housing 33 by the first slot 40.
  • the displacement of the separating element 34 is limited in the direction of the pressure medium channel 30 by an annular, radially inwardly extending portion of the guide housing 33 which surrounds a housing opening 38 through which the volume memory 15 pressure medium can be supplied. In the direction of the spring bearing 39, the displacement of the separating element 34 is limited by a stop.
  • the abutment is embodied between the axial ends of the guide housing 33 in the form of three indentations 41, which are formed integrally with the guide housing 33 and protrude into this ( Figures 4-6 ). Also conceivable are embodiments with more or fewer indentations.
  • Each indentation 41 has an open end on the side facing the separating element 34, the open end having a surface perpendicular to the direction of movement of the separating element 34.
  • the preparation of the indentations 41 takes place in two stages. First, a second slot 42 is inserted into the guide housing 33, which extends in the circumferential direction of the guide housing 33. Subsequently, the material of the guide housing 33 in the region of the second slot 42 is plastically deformed into the guide housing and thus the indentation 41 is formed.
  • Each indentation 41 projects into the guide housing 33 in such a way that the open end faces the open end of the jacket section 26 of the separating element 34 in its direction of displacement. Thus, these open ends of the indentations 41 serve the separation element 34 as a stop.
  • each indentation 41 has a guide portion 43 which extends in the axial direction and parallel to the axis of the spring element 35 runs.
  • the diameter of the spring element 35 is selected so that it bears against the guide sections 43 in the compressed state.
  • the spring element 35 experiences by the guide portions 43 a bearing, whereby the radial position of the spring element 35 is fixed.
  • the length L of the guide portion 43 is greater than the distance between two spring coils in the relaxed state. This ensures that due to the bearing of the spring element 35 on the guide portions 43, the spring element 35 is not tilted or jammed on the stop of the indentation 41.
  • the guide housing 33 and the separating element 34 are formed as sheet metal parts, which are made for example by a non-cutting manufacturing process, for example, a deep drawing process.
  • this has the advantage that the bearing surfaces of the jacket section 26 and of the guide housing 33 can be produced so precisely by this shaping process that they do not have to be reworked.
  • the second slot 42 describes a curved line with two ends, so that a tab 44 is formed, which projects into the guide housing 33.
  • a volume memory 15 is in FIG. 7 shown in a perspective view.
  • a rectangular tab 44 is formed by a U-shaped second slot 42, which projects into the guide housing 33.
  • a leg of the U-shaped slot 42 extends in a plane perpendicular to the direction of movement of the separating element 34, so that the stop is formed.
  • the tab 44 merges into the guide housing 33 in the axial direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Volumenspeicher mit einem Führungsgehäuse und einem Trennelement, wobei das Trennelement an einer Inneren Mantelfläche des Führungsgehäuses verschiebbar gelagert ist.The invention relates to a volume accumulator with a guide housing and a separating element, wherein the separating element is displaceably mounted on an inner circumferential surface of the guide housing.

Hintergrund der ErfindungBackground of the invention

Volumenspeicher werden beispielsweise in Brennkraftmaschinen eingesetzt um die Druckmittelversorgung eines hydraulischen Verbrauchers, beispielsweise eines Nockenwellenverstellers oder einer elektrohydraulischen Ventilbetätigungsvorrichtung, zu unterstützen. Nockenwellenversteller sind beispielsweise aus der DE 195 29 277 A1 oder der EP 0 806 550 A1 bekannt.
Ein Volumenspeicher ist beispielsweise in der DE 10 2007 041 552 A1 offenbart. Der Volumenspeicher weist ein hohlzylindrisches Führungsgehäuse und ein in dem Führungsgehäuse axial verschiebbar aufgenommenes Trennelement, in der dargestellten Ausführungsform einen topfförmigen Kolben auf, das das Innere des Führungsgehäuses in einen Vorratsraum und einen Komplementärraum teilt. Durch Druckmittelbeaufschlagung des Kolbens wir dieser gegen die Kraft eines Federelements in Richtung eines Anschlags verschoben, wodurch das Volumen des Vorratsraums auf Kosten des Volumens des Komplementärraums zunimmt. Dabei wird der Verschiebeweg des Kolbens dadurch begrenzt, dass ein offenes Ende eines Mantelabschnitts des topfförmig ausgebildeten Kolbens an einem ringförmigen, separat zu dem Führungsgehäuse ausgebildeten Anschlag zur Anlage kommt. Der ringförmige Anschlag liegt an einer radial verlaufenden Wandung an einem axialen Ende des Führungsgehäuses an, an der sich gleichzeitig das Federelement abstützt.Volume accumulators are used, for example, in internal combustion engines to support the pressure medium supply of a hydraulic consumer, for example a camshaft adjuster or an electrohydraulic valve actuation device. Camshaft adjusters are for example from the DE 195 29 277 A1 or the EP 0 806 550 A1 known.
A volume memory is for example in the DE 10 2007 041 552 A1 disclosed. The volume accumulator has a hollow-cylindrical guide housing and a separating element received axially displaceably in the guide housing, in the illustrated embodiment a cup-shaped piston which divides the interior of the guide housing into a storage space and a complementary space. By pressurizing the piston, it is displaced against the force of a spring element in the direction of a stop, whereby the volume of the storage space increases at the expense of the volume of the complementary space. In this case, the displacement of the piston is limited by the fact that an open end of a shell portion of the cup-shaped piston comes to rest on an annular, formed separately to the guide housing stop. The annular stop abuts a radially extending wall at an axial end of the guide housing, at the same time the spring element is supported.

Aufgabe der ErfindungObject of the invention

Der Erfindung liegt die Aufgabe zugrunde einen Volumenspeicher zu schaffen, wobei dessen Herstellungsaufwand reduziert werden soll.The invention has for its object to provide a volume storage, the production cost is to be reduced.

Lösung der AufgabeSolution of the task

Die Aufgabe wird erfindungsgemäß dadurch gelöst, dass an dem Führungsgehäuse zumindest eine Einbuchtung ausgebildet ist, die in das Führungsgehäuse hineinragt, wobei die Einbuchtung in Richtung des Trennelements ein offenes Ende aufweist, das als Anschlag für das Trennelement dient.The object is achieved in that at least one indentation is formed on the guide housing, which projects into the guide housing, wherein the indentation in the direction of the separating element has an open end, which serves as a stop for the separating element.

Der Volumenspeicher weist ein Trennelement, beispielsweise einen Kolben, auf, das innerhalb eines Führungsgehäuses verschiebbar gelagert ist, und einen Vorratsraum von einem Komplementärraum trennt. Durch Druckmittelbeaufschlagung des Trennelements wird dieses innerhalb des Führungsgehäuses in Richtung eines Anschlags verschoben, der den Verschiebweg des Trennelements dadurch begrenzt, dass dieses an dem Anschlag zur Anlage kommt. Der Anschlag sichert das Trennelement gegen einen ungewollten Austritt aus dem Führungsgehäuse während dessen Betrieb. Des Weiteren können durch geeignete Positionierung des Anschlags zwischen den Enden des Führungsgehäuses geeignete Federstärken und Federlängen genutzt und so die Volumenspeichercharakteristika geeignet ausgelegt werden.
Dabei ist vorgesehen, dass der Anschlag aus dem Material des Führungsgehäuses ausgebildet wird. Zu diesem Zweck ist ein Schlitz in dem beispielsweise hohlzylindrisch ausgebildeten Führungsgehäuse vorgesehen, der entlang einer nicht in sich geschlossenen Linie verläuft. Dabei verläuft der Schlitz zumindest bereichsweise in einer Ebene senkrecht zu der Verschiebrichtung des Kolbens. Der Schlitz kann beispielsweise durch Stanzen oder Feinschneiden in das Führungsgehäuse eingebracht werden. Im Bereich des Schlitzes ist an dem Führungsgehäuse eine Einbuchtung vorgesehen, die in das Innere des Führungsgehäuses hineinragt. Dabei steht ein durch den Schlitz erzeugtes offenes Ende der Einbuchtung dem Kolben gegenüber und dient diesem als Anschlag. Unter dem offenen Ende ist der Bereich zu verstehen, der vor dem Einbringen des Schlitzes in das Führungsgehäuse mit diesem verbunden war. In dieser Ausführungsform ist der Anschlag zum Einen einteilig mit dem Führungsgehäuse ausgebildet, so dass keine zusätzlichen Bauteile benötigt werden. Zum Anderen besteht keine stoffliche Verbindung zwischen der Anschlagsfläche und dem in Richtung des Kolbens liegenden Bereichs des Führungsgehäuses, so dass dieser Übergangsbereich rechtwinklig, ohne Radius oder Phase, ausgebildet ist. Somit ist sichergestellt, dass sich das Trennelement nicht an dem Anschlag verklemmt. Des Weiteren wird durch die Anlage zweier senkrecht zur Verschieberichtung angeordneter Flächen verhindert, dass der Kolben unter die Einbuchtung abtaucht und verklemmt oder die Einbuchtung nach außen gedrückt wird.
Die Einbuchtung kann eine Vielzahl von Formen annehmen. Denkbar sind beispielsweise Ausführungsformen, in denen ein Schlitz in das Führungsgehäuse eingebracht wird, welcher komplett in einer Ebene senkrecht zu der Verschieberichtung des Kolbens angeordnet ist. Anschließend wird die Einbuchtung im Bereich des Schlitzes in das Führungsgehäuse eingebracht.
Ebenso denkbar sind Ausführungsformen, in denen die Einbuchtung als Lasche ausgebildet ist. Dabei wird ein von einer geraden Linie abweichender Schlitz in das Führungsgehäuse eingebracht, der eine mit dem Führungsgehäuse verbundene Lasche ausbildet. Diese kann beispielsweise dreieckig oder viereckig und gegebenenfalls entsprechend der Form des Führungsgehäuses gewölbt ausgebildet sein und ragt in das Führungsgehäuse hinein.The volume accumulator has a separating element, for example a piston, which is displaceably mounted within a guide housing and separates a storage space from a complementary space. By applying pressure medium to the separating element, the latter is displaced within the guide housing in the direction of a stop which limits the displacement path of the separating element in that it comes into contact with the stop. The stop secures the separator against unwanted leakage from the guide housing during its operation. Furthermore, by suitable positioning of the stop between the ends of the guide housing suitable spring strengths and spring lengths can be used and so the volume storage characteristics are designed appropriately.
It is provided that the stopper is formed from the material of the guide housing. For this purpose, a slot is provided in the example, hollow cylindrical guide housing, which runs along a non-self-contained line. The slot extends at least partially in a plane perpendicular to the direction of displacement of the piston. The slot can be introduced, for example, by punching or fine cutting in the guide housing. In the area of the slot is on the guide housing provided a recess which projects into the interior of the guide housing. In this case, an open end of the indentation created by the slot is opposite the piston and serves as a stop. By the open end is meant the area which was connected to the guide housing prior to the insertion of the slot. In this embodiment, the stop is on the one hand formed integrally with the guide housing, so that no additional components are needed. On the other hand, there is no material connection between the abutment surface and the region of the guide housing lying in the direction of the piston, so that this transition region is formed at right angles, without radius or phase. This ensures that the separating element does not jam against the stop. Furthermore, it is prevented by the arrangement of two surfaces arranged perpendicular to the direction of displacement that the piston dips under the indentation and jammed or the indentation is pushed outward.
The indentation can take a variety of forms. Conceivable, for example, embodiments in which a slot is introduced into the guide housing, which is arranged completely in a plane perpendicular to the direction of displacement of the piston. Subsequently, the indentation is introduced in the region of the slot in the guide housing.
Likewise conceivable are embodiments in which the indentation is designed as a tab. In this case, a deviating from a straight line slot is introduced into the guide housing, which forms a connected to the guide housing tab. This can for example be triangular or square and optionally arched according to the shape of the guide housing and protrudes into the guide housing.

In einer Konkretisierung der Erfindung wird vorgeschlagen, dass in dem Führungsgehäuse ein Federelement angeordnet ist, welches den Bereich der Einbuchtung durchgreift, wobei die Einbuchtung einen Führungsabschnitt für das Federelement aufweist, dessen Länge in Kraftrichtung des Federelementsgrößer als der Abstand zwischen zwei Windungen des Federelements ist. Der Führungsabschnitt stellt eine Führungsfläche für das Federelement bereit, das den Kolben gegen die Kraft des Druckmittels mit einer Kraft beaufschlagt. Das Federelement kann beispielsweise als Schrauben- oder Spiraldruckfeder ausgebildet sein. Dabei ist durch die geeignete Wahl der Länge des Führungsabschnitts sichergestellt, dass immer eine Windung des Federelements in diesem Bereich angeordnet ist und somit das Federelement ausreichend geführt wird, so dass die Federwindungen nicht an dem Anschlag der Lasche verkanten. Das Trennelement kann beispielsweise als topfförmiger Kolben mit einem Boden und einem sich daran anschließenden Mantelabschnitt ausgebildet sein. Vorteilhafterweise sind das Führungsgehäuse und der Kolben spanlos aus jeweils einem Blechrohling, beispielsweise mittels eines Tiefziehverfahrens, hergestellt. Dabei können der Mantelabschnitt des Kolbens und die Innenmantelfläche des Führungsgehäuses beispielsweise zylindrisch oder im Querschnitt polygonförmig ausgebildet sein. Der Boden des Kolbens dient als Druckfläche, die von dem einströmenden Druckmittel mit einer Kraft beaufschlagt wird, wodurch der Kolben verschoben wird. Die Mantelfläche dient zur Lagerung des Kolbens in dem Führungsgehäuse, wobei das offene Ende des Mantelabschnitts bei vollständig befülltem Volumenspeicher in Anlage an den Anschlag kommt. Darüber hinaus erfolgt die Abdichtung des Vorratsraums gegenüber dem Komplementärraum über ein eng toleriertes Spiel zwischen dem Mantelabschnitt und der Innenmantelfläche des Führungsgehäuses.In a concretization of the invention it is proposed that in the guide housing, a spring element is arranged, which passes through the region of the recess, wherein the indentation has a guide portion for the spring element whose length in the direction of force of the spring element is greater than the distance between two turns of the spring element. The guide portion provides a guide surface for the spring element, the the piston against the force of the pressure medium applied with a force. The spring element may be formed, for example, as a helical or helical compression spring. It is ensured by the appropriate choice of the length of the guide portion that always one turn of the spring element is arranged in this area and thus the spring element is sufficiently guided so that the spring coils do not tilt on the stop of the tab. The separating element can be designed, for example, as a cup-shaped piston with a bottom and a shell section adjoining it. Advantageously, the guide housing and the piston without cutting are each made of a sheet metal blank, for example by means of a deep drawing process. In this case, the jacket portion of the piston and the inner circumferential surface of the guide housing may be formed, for example, cylindrical or polygonal in cross-section. The bottom of the piston serves as a pressure surface, which is acted upon by the inflowing pressure medium with a force, whereby the piston is displaced. The lateral surface serves to support the piston in the guide housing, with the open end of the jacket section coming into contact with the stop when the volume reservoir is completely filled. In addition, the sealing of the storage space relative to the complementary space via a closely tolerated clearance between the shell portion and the inner circumferential surface of the guide housing.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen in denen Ausführungsbeispiele der Erfindung vereinfacht dargestellt sind. Es zeigen:

Figur 1
nur sehr schematisch eine Brennkraftmaschine,
Figur 2
einen Längsschnitt durch einen Nockenwellenversteller, der an einer Nockenwelle befestigt ist, in der eine erste Ausführungsform eines Volumenspeichers angeordnet ist,
Figur 3
einen Querschnitt durch den Nockenwellenversteller aus Figur 2 entlang der Linie III-III, wobei die Zentralschraube nicht dargestellt ist,
Figur 4
die Einzelheit X aus Figur 2 ohne Nockenwelle,
Figur 5
einen Querschnitt durch den Volumenspeicher entlang der Linie V-V in Figur 4,
Figur 6
einen perspektivische Ansicht der ersten Ausführungsform eines Volumenspeichers,
Figur 7
einen perspektivische Ansicht einer zweiten Ausführungsform eines Volumenspeichers.
Further features of the invention will become apparent from the following description and from the drawings in which embodiments of the invention are shown in simplified form. Show it:
FIG. 1
only very schematically an internal combustion engine,
FIG. 2
a longitudinal section through a camshaft adjuster, which is fixed to a camshaft, in which a first embodiment of a volume memory is arranged,
FIG. 3
a cross section through the camshaft adjuster FIG. 2 along the line III-III, with the central screw not shown,
FIG. 4
the detail X out FIG. 2 without camshaft,
FIG. 5
a cross section through the volume storage along the line VV in FIG. 4 .
FIG. 6
a perspective view of the first embodiment of a volume memory,
FIG. 7
a perspective view of a second embodiment of a volume memory.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

In Figur 1 ist eine Brennkraftmaschine 1 skizziert, wobei ein auf einer Kurbelwelle 2 sitzender Kolben 3 in einem Zylinder 4 angedeutet ist. Die Kurbelwelle 2 steht in der dargestellten Ausführungsform über je einen Zugmitteltrieb 5 mit einer Einlassnockenwelle 6 bzw. Auslassnockenwelle 7 in Verbindung, wobei ein erster und ein zweiter Nockenwellenversteller 11 für eine Relativdrehung zwischen der Kurbelwelle 2 und den Nockenwellen 6, 7 sorgen können. Nocken 8 der Nockenwellen 6, 7 betätigen ein oder mehrere Einlassgaswechselventile 9 bzw. ein oder mehrere Auslassgaswechselventile 10. Ebenso kann vorgesehen sein nur eine der Nockenwellen 6, 7 mit einem Nockenwellenversteller 11 auszustatten, oder nur eine Nockenwelle 6, 7 vorzusehen, welche mit einem Nockenwellenversteller 11 versehen ist.In FIG. 1 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4. The crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second camshaft adjuster 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide. Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslassgaswechselventile 10. Also can be provided only one of the camshafts 6, 7 with a camshaft adjuster 11 equip, or only a camshaft 6, 7 provide, which with a Camshaft adjuster 11 is provided.

Die Figuren 2 und 3 zeigen einen Nockenwellenversteller 11 im Längs- bzw. im Querschnitt. Darüberhinaus zeigt Figur 2 einen Volumenspeicher 15, der in einer Nockenwelle 6, 7 angeordnet ist, die drehfest mit dem Nockenwellenversteller 11 verbunden ist.
Der Nockenwellenversteller 11 umfasst ein Antriebselement 14, ein Abtriebselement 16 und zwei Seitendeckel 17, 18, die an den axialen Seitenflächen des Antriebselements 14 angeordnet sind. Das Abtriebselement 16 ist in Form eines Flügelrades ausgeführt und weist ein im Wesentlichen zylindrisch ausgeführtes Nabenelement 19 auf, von dessen äußerer zylindrischer Mantelfläche sich in der dargestellten Ausführungsform fünf Flügel 20 in radialer Richtung nach außen erstrecken.
Innerhalb des Nockenwellenverstellers 11 sind fünf Druckräume 22 vorgesehen, wobei in jeden Druckraum 22 ein Flügel 20 ragt. Dabei sind die Flügel 20 derart ausgebildet, dass diese sowohl an den Seitendeckeln 17, 18, als auch an der Umfangswand 21 anliegen. Jeder Flügel 20 teilt somit den jeweiligen Druckraum 22 in zwei gegeneinander wirkende Druckkammern 23, 24.
An einer äußeren Mantelfläche des Antriebselements 14 ist ein Kettenrad 12 ausgebildet, über das mittels eines nicht dargestellten Kettentriebs Drehmoment von der Kurbelwelle 2 auf das Antriebselement 14 übertragen werden kann. Das Abtriebselement 16 ist mittels einer Zentralschraube 13 drehfest mit der Nockenwelle 6,7 verbunden.The Figures 2 and 3 show a camshaft adjuster 11 in longitudinal or in cross section. In addition shows FIG. 2 a volume accumulator 15, which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 11.
The phaser 11 includes a drive element 14, an output element 16 and two side covers 17, 18 which are arranged on the axial side surfaces of the drive element 14. The output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 19, extend from the outer cylindrical surface in the illustrated embodiment, five wings 20 in the radial direction outwardly.
Within the camshaft adjuster 11 five pressure chambers 22 are provided, wherein in each pressure chamber 22, a wing 20 protrudes. In this case, the wings 20 are formed such that they rest against both the side covers 17, 18, and on the peripheral wall 21. Each wing 20 thus divides the respective pressure chamber 22 into two counteracting pressure chambers 23, 24th
On an outer circumferential surface of the drive element 14, a sprocket 12 is formed, via which by means of a chain drive, not shown, torque from the crankshaft 2 to the drive element 14 can be transmitted. The output member 16 is rotatably connected by means of a central screw 13 with the camshaft 6,7.

Das Abtriebselement 16 ist in einem definierten Winkelbreich drehbar zu dem Antriebselement 14 angeordnet. Durch Druckmittelzufuhr zu einer Gruppe von Druckkammern 23, 24 und Druckmittelabfuhr von der anderen Gruppe kann die Phasenlage des Antriebselements 14 zum Abtriebselement 16 (und damit die Phasenlage der Nockenwelle 6, 7 zur Kurbelwelle 2) variiert werden. Durch Druckmittelzufuhr zu beiden Gruppen von Druckkammern 23, 24 kann die Phasenlage konstant gehalten werden.The output element 16 is arranged rotatably in a defined Winkelbreich to the drive element 14. By supplying pressure medium to a group of pressure chambers 23, 24 and pressure medium discharge from the other group, the phase position of the drive element 14 to the output element 16 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied. By supplying pressure medium to both groups of pressure chambers 23, 24, the phase position can be kept constant.

Die Nockenwelle 6, 7 weist im Bereich eines Nockenwellenlagers 32 mehrere Öffnungen 28 auf, über die von einer Druckmittelpumpe 37 gefördertes Druckmittel in deren Inneres gelangt. Innerhalb der Nockenwelle 6, 7 ist ein Druckmittelpfad 29 ausgebildet, der einerseits mit den Öffnungen 28 und andererseits mit einem Steuerventil 27 kommuniziert, das zur Versorgung des Nockenwellenverstellers 11 mit Druckmittel dient. Das Steuerventil 27 ist im Inneren der Zentralschraube 13 angeordnet. Mittels des Steuerventils 27 kann Druckmittel wahlweise zu den ersten oder zweiten Druckkammern 23, 24 geleitet und von den jeweils anderen Druckkammern 23, 24 abgeführt werden.In the region of a camshaft bearing 32, the camshaft 6, 7 has a plurality of openings 28, via which pressure medium conveyed by a pressure medium pump 37 passes into its interior. Within the camshaft 6, 7 is a pressure medium path 29 formed on the one hand communicates with the openings 28 and on the other hand with a control valve 27 which serves to supply the camshaft adjuster 11 with pressure medium. The control valve 27 is arranged in the interior of the central screw 13. By means of the control valve 27, pressure medium can be selectively directed to the first or second pressure chambers 23, 24 and discharged from the respective other pressure chambers 23, 24.

Im Inneren der Zentralschraube 13 ist ein Druckmittelkanal 30 vorgesehen, der einerseits mit dem Druckmittelpfad 29 und andererseits mit einem Hohlraum 31 der hohl ausgebildeten Nockenwelle 6, 7 kommuniziert. Der Druckmittelkanal 30 ist als axiale Bohrung ausgebildet, die den Gewindeabschnitt der Zentralschraube 13 durchgreift.
In dem Hohlraum 31 ist der Volumenspeicher 15 angeordnet. Der Volumenspeicher 15 umfasst ein Führungsgehäuse 33, ein Trennelement 34 und einen Kraftspeicher, der in der dargestellten Ausführungsform als Federelement 35 in Form einer Schraubendruckfeder ausgeführt ist. Das Führungsgehäuse 33 ist kraftschlüssig mit einer Wandung 36 des Hohlraums 31 verbunden. Denkbar sind auch Ausführungsformen, in denen das Führungsgehäuse 33 stoff- oder formschlüssig mit der Wandung 36 verbunden ist.
Im Inneren des Führungsgehäuses 33 ist das Trennelement 34 axial verschiebbar angeordnet, wobei dieses in der dargestellten Ausführungsform als topfförmiger Kolben mit einem Boden 25 und einem Mantelabschnitt 26 ausgebildet ist. Mittels des Mantelabschnitts 26 ist das Trennelement 34 axial verschiebbar in dem Führungsgehäuse 33 gelagert. Die Außenmantelfläche des Trennelements 34 ist der Innenmantelfläche des Führungsgehäuses 33 derart angepasst, dass das Führungsgehäuse 33 druckmitteldicht in einen Vorratsraum 45 axial vor und einen Komplementärraum 46 hinter dem Boden 25 des Trennelements 34 getrennt wird.
Das Federelement 35 stützt sich einerseits an einem Federlager 39 (Figur 4), das an dem dem Nockenwellenversteller 11 abgewandten Ende des Führungsgehäuses 33 ausgebildet ist, und andererseits an dem Boden 25 des Trennelements 34 ab. Somit beaufschlagt das Federelement 35 das Trennelement 34 mit einer Kraft in Richtung des Druckmittelkanals 30. Das Federlager 39 ist als radiale Einbuchtung 47 des Führungsgehäuses 33 ausgebildet. Zu diesem Zweck ist in das zylindrische Führungsgehäuse 33 ein erster Schlitz 40 eingebracht, der in Umfangsrichtung des Führungsgehäuses 33 verläuft. Anschließend wird das Führungsgehäuse 33 in dem Bereich zwischen dem ersten Schlitz 40 und dem nockenwellenabgewandten Ende radial nach innen verformt. Die Tiefe der dadurch erzeugten Einbuchtung 47 ist so gewählt, dass das Federelement 35 selbst bei maximaler Federexzentrizität an dem offenen Ende des Federlagers 39 anliegt, das durch den ersten Schlitz 40 von dem Führungsgehäuse 33 getrennt wurde.Inside the central screw 13, a pressure medium channel 30 is provided, which communicates on the one hand with the pressure medium path 29 and on the other hand with a cavity 31 of the hollow camshaft 6, 7. The pressure medium channel 30 is formed as an axial bore, which passes through the threaded portion of the central screw 13.
In the cavity 31, the volume accumulator 15 is arranged. The volume memory 15 comprises a guide housing 33, a separating element 34 and a force accumulator, which is designed in the illustrated embodiment as a spring element 35 in the form of a helical compression spring. The guide housing 33 is non-positively connected to a wall 36 of the cavity 31. Also conceivable are embodiments in which the guide housing 33 is connected to the wall 36 in a material- or form-fitting manner.
In the interior of the guide housing 33, the separating element 34 is arranged axially displaceable, wherein this is formed in the illustrated embodiment as a cup-shaped piston having a bottom 25 and a jacket portion 26. By means of the jacket section 26, the separating element 34 is mounted axially displaceably in the guide housing 33. The outer lateral surface of the separating element 34 is adapted to the inner lateral surface of the guide housing 33 in such a way that the guide housing 33 is separated in a pressure medium-tight manner into a reservoir 45 axially in front of and a complementary space 46 behind the bottom 25 of the separating element 34.
The spring element 35 is supported on the one hand on a spring bearing 39 (FIG. FIG. 4 ), which is formed on the camshaft adjuster 11 facing away from the end of the guide housing 33, and on the other hand on the bottom 25 of the separating element 34 from. Thus, the spring element 35 acts on the separating element 34 with a force in the direction of the pressure medium channel 30. The spring bearing 39 is formed as a radial indentation 47 of the guide housing 33. For this purpose, a first slot 40 is inserted into the cylindrical guide housing 33, which extends in the circumferential direction of the guide housing 33. Subsequently, the guide housing 33 is deformed radially inwardly in the region between the first slot 40 and the end remote from the camshaft. The depth of the indentation 47 produced thereby is selected so that the spring element 35 bears against the open end of the spring bearing 39 even at maximum spring eccentricity, which has been separated from the guide housing 33 by the first slot 40.

Der Verschiebeweg des Trennelements 34 wird in Richtung des Druckmittelkanals 30 durch einen ringförmigen, radial nach innen verlaufenden Abschnitt des Führungsgehäuses 33 begrenzt, der eine Gehäuseöffnung 38 umgreift, durch die dem Volumenspeicher 15 Druckmittel zugeführt werden kann. In Richtung des Federlagers 39 wird der Verschiebeweg des Trennelements 34 durch einen Anschlag begrenzt. Der Anschlag ist zwischen den axialen Enden des Führungsgehäuses 33 in Form von drei Einbuchtungen 41 ausgeführt, die einteilig mit dem Führungsgehäuse 33 ausgebildet sind und in dieses hinein ragen (Figuren 4-6). Ebenso denkbar sind Ausführungsformen mit mehr oder weniger Einbuchtungen. Jede Einbuchtung 41 weist auf der dem Trennelement 34 zugewandten Seite ein offenes Ende auf, wobei das offene Ende eine Fläche senkrecht zur Bewegungsrichtung des Trennelements 34 aufweist. Die Herstellung der Einbuchtungen 41 erfolgt zweistufig. Zunächst wird in das Führungsgehäuse 33 ein zweiter Schlitz 42 eingebracht, der in Umfangsrichtung des Führungsgehäuses 33 verläuft. Anschließend wird das Material des Führungsgehäuses 33 im Bereich des zweiten Schlitzes 42 plastisch in das Führungsgehäuse hinein verformt und so die Einbuchtung 41 ausgebildet.
Jede Einbuchtung 41 ragt derart in das Führungsgehäuse 33 hinein, dass das offene Ende dem offenen Ende des Mantelabschnitts 26 des Trennelements 34 in dessen Verschieberichtung gegenübersteht. Somit dienen diese offenen Enden der Einbuchtungen 41 dem Trennelement 34 als Anschlag.
Darüber hinaus weist jede Einbuchtung 41 einen Führungsabschnitt 43 auf, der sich in axialer Richtung erstreckt und parallel zu der Achse des Federelements 35 verläuft. Dabei ist der Durchmesser des Federelements 35 so gewählt, dass dieses im komprimierten Zustand an den Führungsabschnitten 43 anliegt. Somit erfährt das Federelement 35 durch die Führungsabschnitte 43 eine Lagerung, wodurch die radiale Position des Federelements 35 festgelegt wird. Die Länge L des Führungsabschnitts 43 ist größer als der Abstand zweier Federwindungen im entspannten Zustand. Somit ist sichergestellt, dass auf Grund der Lagerung des Federelements 35 an den Führungsabschnitten 43 das Federelement 35 an dem Anschlag der Einbuchtung 41 nicht verkantet oder klemmt.The displacement of the separating element 34 is limited in the direction of the pressure medium channel 30 by an annular, radially inwardly extending portion of the guide housing 33 which surrounds a housing opening 38 through which the volume memory 15 pressure medium can be supplied. In the direction of the spring bearing 39, the displacement of the separating element 34 is limited by a stop. The abutment is embodied between the axial ends of the guide housing 33 in the form of three indentations 41, which are formed integrally with the guide housing 33 and protrude into this ( Figures 4-6 ). Also conceivable are embodiments with more or fewer indentations. Each indentation 41 has an open end on the side facing the separating element 34, the open end having a surface perpendicular to the direction of movement of the separating element 34. The preparation of the indentations 41 takes place in two stages. First, a second slot 42 is inserted into the guide housing 33, which extends in the circumferential direction of the guide housing 33. Subsequently, the material of the guide housing 33 in the region of the second slot 42 is plastically deformed into the guide housing and thus the indentation 41 is formed.
Each indentation 41 projects into the guide housing 33 in such a way that the open end faces the open end of the jacket section 26 of the separating element 34 in its direction of displacement. Thus, these open ends of the indentations 41 serve the separation element 34 as a stop.
In addition, each indentation 41 has a guide portion 43 which extends in the axial direction and parallel to the axis of the spring element 35 runs. In this case, the diameter of the spring element 35 is selected so that it bears against the guide sections 43 in the compressed state. Thus, the spring element 35 experiences by the guide portions 43 a bearing, whereby the radial position of the spring element 35 is fixed. The length L of the guide portion 43 is greater than the distance between two spring coils in the relaxed state. This ensures that due to the bearing of the spring element 35 on the guide portions 43, the spring element 35 is not tilted or jammed on the stop of the indentation 41.

In der dargestellten Ausführungsform sind das Führungsgehäuse 33 und das Trennelement 34 als Blechteile ausgebildet, die beispielsweise durch ein spanloses Herstellungsverfahren, beispielsweise einem Tiefziehverfahren, hergestellt sind. Dies hat neben geringen Herstellungskosten den Vorteil, dass die Lagerflächen des Mantelabschnitts 26 und des Führungsgehäuses 33 durch diesen Formgebungsprozess so präzise herstellbar sind, dass diese nicht nachbearbeitet werden müssen.In the illustrated embodiment, the guide housing 33 and the separating element 34 are formed as sheet metal parts, which are made for example by a non-cutting manufacturing process, for example, a deep drawing process. In addition to low manufacturing costs, this has the advantage that the bearing surfaces of the jacket section 26 and of the guide housing 33 can be produced so precisely by this shaping process that they do not have to be reworked.

In einer alternativen Ausführungsform eines Volumenspeichers 15 beschreibt der zweite Schlitz 42 eine gebogene Linie mit zwei Enden, so dass eine Lasche 44 ausgebildet ist, die in das Führungsgehäuse 33 hineinragt. Ein derartiger Volumenspeicher 15 ist in Figur 7 in einer perspektivischen Ansicht dargestellt. In dieser Ausführungsform ist durch einen U-förmigen zweiten Schlitz 42 eine rechteckige Lasche 44 ausgebildet, welche in das Führungsgehäuse 33 hineinragt. Dabei verläuft ein Schenkel des U-förmigen Schlitzes 42 in einer Ebene senkrecht zu der Bewegungsrichtung des Trennelements 34, so dass der Anschlag ausgebildet ist. Neben der in Figur 7 dargestellten Ausführungsform, in der die Lasche 44 in Umfangsrichtung mit dem Führungsgehäuse 33 verbunden ist, sind auch Ausführungsformen denkbar, in denen die Lasche 44 in axialer Richtung in das Führungsgehäuse 33 übergeht.In an alternative embodiment of a volume memory 15, the second slot 42 describes a curved line with two ends, so that a tab 44 is formed, which projects into the guide housing 33. Such a volume memory 15 is in FIG. 7 shown in a perspective view. In this embodiment, a rectangular tab 44 is formed by a U-shaped second slot 42, which projects into the guide housing 33. In this case, a leg of the U-shaped slot 42 extends in a plane perpendicular to the direction of movement of the separating element 34, so that the stop is formed. In addition to the in FIG. 7 illustrated embodiment in which the tab 44 is connected in the circumferential direction with the guide housing 33, embodiments are also conceivable in which the tab 44 merges into the guide housing 33 in the axial direction.

Bezugszeichenreference numeral

11
BrennkraftmaschineInternal combustion engine
22
Kurbelwellecrankshaft
33
Kolbenpiston
44
Zylindercylinder
55
Zugmitteltriebtraction drive
66
Einlassnockenwelleintake camshaft
77
Auslassnockenwelleexhaust
88th
Nockencam
99
EinlassgaswechselventilInlet gas exchange valve
1010
AuslassgaswechselventilAuslassgaswechselventil
1111
NockenwellenverstellerPhaser
1212
KettenradSprocket
1313
Zentralschraubecentral screw
1414
Antriebselementdriving element
1515
Volumenspeichervolume storage
1616
Abtriebselementoutput element
1717
Seitendeckelside cover
1818
Seitendeckelside cover
1919
Nabenelementhub element
2020
Flügelwing
2121
Umfangswandperipheral wall
2222
Druckraumpressure chamber
2323
erste Druckkammerfirst pressure chamber
2424
zweite Druckkammersecond pressure chamber
2525
Bodenground
2626
Mantelabschnittshell section
2727
Steuerventilcontrol valve
2828
Öffnungenopenings
2929
DruckmittelpfadPressure fluid conduit
3030
DruckmittelkanalPressure fluid channel
3131
Hohlraumcavity
3232
Nockenwellenlagercamshaft bearings
3333
Führungsgehäuseguide housing
3434
Trennelementseparating element
3535
Federelementspring element
3636
Wandungwall
3737
DruckmittelpumpeHydraulic pump
3838
Gehäuseöffnunghousing opening
3939
Federlagerspring camp
4040
erster Schlitzfirst slot
4141
Einbuchtungindentation
4242
zweiter Schlitzsecond slot
4343
Führungsabschnittguide section
4444
Lascheflap
4545
Vorratsraumpantry
4646
Komplementärraumcomplementary space
4747
Einbuchtungindentation
LL
Längelength

Claims (3)

  1. Volume accumulator (15) having a guide housing (33) and a dividing element (34), wherein the dividing element (34) is mounted in a displaceable manner on an inner lateral surface of the guide housing (33),
    characterized in that at least one indentation (41) is formed on the guide housing (33), which indentation projects into the guide housing (33), wherein the indentation (41) has, in the direction of the dividing element (34), an open end which serves as a stop for the dividing element (34).
  2. Volume accumulator (15) according to Claim 1, characterized in that a spring element (35) is arranged in the guide housing (33), which spring element extends through the region of the indentation (41), wherein the indentation (41) has a guide portion (43) for the spring element (35), the length of which guide portion in the direction of force of the spring element (35) is greater than the spacing between two windings of the spring element (35).
  3. Volume accumulator (15) according to Claim 1, characterized in that the indentation (41) is formed as a lug (44).
EP20100781450 2009-10-15 2010-10-14 Volume accumulator Not-in-force EP2488731B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049459A DE102009049459A1 (en) 2009-10-15 2009-10-15 volume storage
PCT/EP2010/065402 WO2011045369A1 (en) 2009-10-15 2010-10-14 Volume accumulator

Publications (2)

Publication Number Publication Date
EP2488731A1 EP2488731A1 (en) 2012-08-22
EP2488731B1 true EP2488731B1 (en) 2014-09-03

Family

ID=43500227

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100781450 Not-in-force EP2488731B1 (en) 2009-10-15 2010-10-14 Volume accumulator

Country Status (5)

Country Link
US (1) US8707998B2 (en)
EP (1) EP2488731B1 (en)
CN (1) CN102549242B (en)
DE (1) DE102009049459A1 (en)
WO (1) WO2011045369A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010018203A1 (en) 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Pressure accumulator arrangement for a camshaft adjusting system
DE102011075537A1 (en) * 2011-05-10 2012-11-15 Schaeffler Technologies AG & Co. KG Reciprocating internal combustion engine with camshaft adjusting device
DE102012201558B4 (en) * 2012-02-02 2017-09-07 Schaeffler Technologies AG & Co. KG Design of a tank connection in a camshaft adjuster with volume memory

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8430562D0 (en) 1984-12-04 1985-01-09 Carpenter & Paterson Ltd Spring support device
DE3705642A1 (en) 1986-07-02 1988-01-14 Man Nutzfahrzeuge Gmbh ENERGY STORAGE AND DELIVERY DEVICE
DE3633836C1 (en) * 1986-10-04 1988-03-31 Ford Werke Ag Temperature-compensated control valve, in particular an accumulator valve for hydraulic control of motor vehicle transmissions
DE3941241C2 (en) * 1989-12-14 2002-03-21 Continental Teves Ag & Co Ohg Piston pressure accumulator, in particular for brake systems controlled by drive slip, and a switching arrangement therefor
DE4234217C2 (en) 1992-10-10 1996-07-11 Hemscheidt Fahrwerktech Gmbh Hydropneumatic suspension system
JP3212384B2 (en) * 1992-11-11 2001-09-25 株式会社ニチリン accumulator
DE19529277A1 (en) 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Method for operating a hydraulically controlled / regulated camshaft adjusting device for internal combustion engines
FR2740528B1 (en) 1995-10-30 1999-09-17 Bernard Claude Andre Francois ASSEMBLY DEVICE FOR ELASTIC MOBILE LOAD SUPPORTS
EP2320037B8 (en) 1996-03-28 2013-11-13 Aisin Seiki Kabushiki Kaisha Camshaft phasing device
DE19725240A1 (en) 1997-06-14 1998-12-17 Itt Mfg Enterprises Inc Pressure medium storage for hydraulic sets of vehicle electronic braking systems
US5996632A (en) * 1998-12-14 1999-12-07 Aeroquip Corporation Pressure relief adapter
DE102005015262A1 (en) * 2005-04-04 2006-10-05 Robert Bosch Gmbh Pressurized medium accumulator for electronically slip-regulated vehicle brake assembly, has piston with gasket that divides accumulator into separate chambers, where piston is single-piece chipless component made of sheet metal material
DE102007041552A1 (en) 2007-08-31 2009-03-05 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
US9038668B2 (en) * 2010-03-16 2015-05-26 Gm Global Technology Operations, Llc Accumulator assembly

Also Published As

Publication number Publication date
CN102549242B (en) 2014-04-09
US20120199230A1 (en) 2012-08-09
EP2488731A1 (en) 2012-08-22
DE102009049459A1 (en) 2011-04-21
WO2011045369A1 (en) 2011-04-21
US8707998B2 (en) 2014-04-29
CN102549242A (en) 2012-07-04

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