EP2488730A1 - Volume accumulator - Google Patents

Volume accumulator

Info

Publication number
EP2488730A1
EP2488730A1 EP10773600A EP10773600A EP2488730A1 EP 2488730 A1 EP2488730 A1 EP 2488730A1 EP 10773600 A EP10773600 A EP 10773600A EP 10773600 A EP10773600 A EP 10773600A EP 2488730 A1 EP2488730 A1 EP 2488730A1
Authority
EP
European Patent Office
Prior art keywords
guide housing
indentation
spring element
separating 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.)
Granted
Application number
EP10773600A
Other languages
German (de)
French (fr)
Other versions
EP2488730B1 (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 EP2488730A1 publication Critical patent/EP2488730A1/en
Application granted granted Critical
Publication of EP2488730B1 publication Critical patent/EP2488730B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • 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

Definitions

  • the invention relates to a volume accumulator having a guide housing, a separating element and a spring element, wherein the separating element is displaceably mounted on an inner lateral surface of the guide housing and the spring element rests on the one hand on the separating element and on the other hand on 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 known, for example, from DE 195 29 277 A1 or EP 0 806 550 A1.
  • a volume memory is disclosed, for example, in DE 10 2007 041 552 A1.
  • 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.
  • a cup-shaped piston which divides the interior of the guide housing into a storage space and a complementary space.
  • 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 foundedsgefeldu- se, wherein the indentation in the direction of the spring element has an open end against which abuts the spring element.
  • the volume accumulator has a separating element, for example a piston, on which is displaceably mounted within a guide housing and separates a storage space from a complementary space.
  • a separating element for example a piston
  • This is displaced within the guide housing against a spring element in the direction of a stop, which limits the displacement path of the separating element in that this comes to rest against the stop.
  • a spring bearing is provided, wherein the spring element is supported on the one hand on the spring bearing and on the other hand on the separating element.
  • the spring bearing 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 produced by the slot faces the end of the spring element and serves this as a spring bearing.
  • Conceivable are embodiments with one or more circumferentially spaced indentations. By the open end is meant the area which was connected to the guide housing prior to the insertion of the slot.
  • the spring bearing is formed integrally with the guide housing, so that no additional components are required, which must be connected to the guide housing.
  • the introduction of the indentation can be realized inexpensively.
  • the indentation can take a variety of forms. Embodiments are conceivable, for example, in which a slot is made in the guide housing, which is arranged completely in a plane perpendicular to the displacement direction 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 slot deviating from a straight line is introduced into the guide housing, which forms a tab connected to the guide housing.
  • 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.
  • the separating element can be designed, for example, as a cup-shaped piston with a base and a jacket section adjoining it, the spring element resting against the base.
  • 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 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.
  • FIG. 1 shows very schematically an internal combustion engine
  • FIG. 2 shows a longitudinal section through a camshaft adjuster, which is fastened to a camshaft, in which a first embodiment of a volume accumulator is arranged
  • FIG. 3 shows a cross section through the camshaft adjuster from FIG. 2 along the line III-III, the central screw not being shown, FIG.
  • FIG. 4 shows detail X from FIG. 2 without camshaft
  • Figure 5 shows a cross section through the volume storage along the line
  • Figure 6 is a perspective view of the first embodiment of a
  • Figure 7 is a perspective view of a second embodiment of a volume memory.
  • FIG. 1 shows 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, wherein a first and a second camshaft adjuster 1 1 for 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 exhaust gas exchange valves 10. Equally, it may be provided only one of the camshafts 6, 7 with a Nockenwellenvers- teller 1 1, or only a camshaft 6, 7 provide, which is provided with a camshaft adjuster 1 1.
  • Figures 2 and 3 show a camshaft adjuster 1 1 in the longitudinal or in the cross section.
  • Figure 2 shows a volume accumulator 15 which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 1 1.
  • the camshaft adjuster 1 1 comprises 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 driven element 16 is designed in the form of an impeller and has a substantially cylindrical hub element 19, from the outer cylindrical surface of which in the illustrated embodiment, five wings 20 extend in the radial direction to the outside.
  • each pressure chamber 22 is 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 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 is formed, which communicates on the one hand with the openings 28 and on the other hand with a control valve 27 which serves to supply the camshaft adjuster 1 1 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 to be axially displaceable, wherein in the illustrated embodiment this is designed as a cup-shaped piston with a bottom 25 and a jacket section 26. miger piston with a bottom 25 and a skirt portion 26 is formed.
  • the jacket section 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. 4), which is formed on the end of the guide housing 33 remote from the camshaft adjuster 11, and on the other hand on the bottom 25 of the separating element 34.
  • the spring bearing 39 is formed by three radial recess 47 of the guide housing 33, which project into this.
  • 33 three first slots 40 are inserted into the cylindrical guide housing, which extend in the circumferential direction of the guide housing 33 and are spaced in the circumferential direction. Subsequently, the guide housing 33 is deformed radially inwardly in the areas between the first slots 40 and the end remote from the camshaft.
  • the depth of the recesses 47 is selected so that the spring element 35 abuts the indentations 47 even at maximum spring eccentricity at the open ends which have been separated from the guide housing 33 by the first slots 40.
  • the spring bearing 39 is formed integrally with the guide housing 33, whereby the manufacturing cost and the manufacturing cost decrease.
  • 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.
  • the displacement of the separating element 34 is limited by a stop.
  • the stop is made 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 project 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 indentations 41 are produced 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 protrudes into the guide housing 33 in such a way that its open end faces the open end of the jacket section 26 of the separating element 34 in its direction of displacement.
  • these open ends of the indentations 41 serve the separation element 34 as a stop.
  • each indentation 41 has a guide section 43 which extends in the axial direction and runs parallel to the axis of the spring element 35.
  • 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. 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.
  • the first slot 40 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 shown in Figure 7 in a perspective view.
  • a rectangular tab 44 is formed by an L-shaped second slot 40, which projects into the guide housing 33.
  • a portion of the L-shaped slot 40 extends in the circumferential direction of the guide housing 33, so that the open end formed thereby serves as a spring bearing 39.
  • the second portion of the L-shaped slot 40 extends to the end of the guide housing 33.

Abstract

The invention relates to a volume accumulator (15), comprising a guide housing (33), a separating element (34) and a spring element (35), wherein the separating element (34) is slidably mounted on an inner lateral face of the guide housing (33) and the spring element (35) is seated against the separating element (34) on one side and on the guide housing (33) on the other side. According to the invention, at least one indentation (47) is designed on the guide housing (33), said indentation protruding into the guide housing (33), wherein in the direction of the spring element (35) the indentation (47) has an open end against which the spring element (35) is seated.

Description

Bezeichnung der Erfindung  Name of the invention
Volumenspeicher Beschreibung Volume memory description
Gebiet der Erfindung Die Erfindung betrifft einen Volumenspeicher mit einem Führungsgehäuse, einem Trennelement und einem Federelement, wobei das Trennelement an einer Inneren Mantelfläche des Führungsgehäuses verschiebbar gelagert ist und das Federelement einerseits an dem Trennelement und andererseits an dem Führungsgehäuse anliegt. FIELD OF THE INVENTION The invention relates to a volume accumulator having a guide housing, a separating element and a spring element, wherein the separating element is displaceably mounted on an inner lateral surface of the guide housing and the spring element rests on the one hand on the separating element and on the other hand on the guide housing.
Hintergrund der Erfindung Background of the invention
Volumenspeicher werden beispielsweise in Brennkraftmaschinen eingesetzt um die Druckmittelversorgung eines hydraulischen Verbrauchers, beispielswei- se 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. 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 known, for example, from DE 195 29 277 A1 or EP 0 806 550 A1.
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. Das Federelement stützt sich einerseits an dem Kolben und andererseits an der radial verlaufenden Wandung des Führungsgehäuses an. A volume memory is disclosed, for example, in DE 10 2007 041 552 A1. 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 jacket portion of the pot-shaped piston on an annular, separate from the guide housing trained stop comes to the plant. The annular stop abuts against a radially extending wall at an axial end of the guide housing. The spring element is supported on the one hand on the piston and on the other hand on the radially extending wall of the guide housing.
Aufgabe der Erfindung Object 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 Aufgabe Solution of the task
Die Aufgabe wird erfindungsgemäß dadurch gelöst, dass an dem Führungsgehäuse zumindest eine Einbuchtung ausgebildet ist, die in das Führungsgehäu- se hineinragt, wobei die Einbuchtung in Richtung des Federelements ein offenes Ende aufweist, an dem das Federelement anliegt. The object is achieved in that at least one indentation is formed on the guide housing, which projects into the Führungsgehäu- se, wherein the indentation in the direction of the spring element has an open end against which abuts the spring 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 gegen ein Federelement in Richtung eines Anschlags verschoben, der den Verschiebweg des Trennelements dadurch begrenzt, dass dieses an dem Anschlag zur Anlage kommt. In Verschieberichtung des Trennelements hinter dem Anschlag ist ein Federlager vorgesehen, wobei sich das Federelement einerseits an dem Federlager und andererseits an dem Trennelement abstützt. Dabei ist vorgesehen, dass das Federlager 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 Ende des Federelements gegenüber und dient diesem als Federlager. Denkbar sind Ausführungsformen mit einer oder mehrerer in Umfangsrichtung beabstandeter Einbuchtungen. Unter dem offenen Ende ist der Bereich zu verstehen, der vor dem Einbringen des Schlitzes in das Führungsgehäuse mit diesem verbunden war. The volume accumulator has a separating element, for example a piston, on which is displaceably mounted within a guide housing and separates a storage space from a complementary space. By applying pressure medium of the separating element, this is displaced within the guide housing against a spring element in the direction of a stop, which limits the displacement path of the separating element in that this comes to rest against the stop. In the direction of displacement of the separating element behind the stop a spring bearing is provided, wherein the spring element is supported on the one hand on the spring bearing and on the other hand on the separating element. It is provided that the spring bearing 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 produced by the slot faces the end of the spring element and serves this as a spring bearing. Conceivable are embodiments with one or more circumferentially spaced indentations. By the open end is meant the area which was connected to the guide housing prior to the insertion of the slot.
In dieser Ausführungsform ist das Federlager einteilig mit dem Führungsgehäuse ausgebildet, so dass keine zusätzlichen Bauteile benötigt werden, die mit dem Führungsgehäuse verbunden werden müssen. Das Einbringen der Einbuchtung kann kostengünstig realisiert werden.  In this embodiment, the spring bearing is formed integrally with the guide housing, so that no additional components are required, which must be connected to the guide housing. The introduction of the indentation can be realized inexpensively.
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 Verschie- berichtung des Kolbens angeordnet ist. Anschließend wird die Einbuchtung im Bereich des Schlitzes in das Führungsgehäuse eingebracht.  The indentation can take a variety of forms. Embodiments are conceivable, for example, in which a slot is made in the guide housing, which is arranged completely in a plane perpendicular to the displacement direction of the piston. Subsequently, the indentation is introduced in the region of the slot in the guide housing.
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 Führungsge- häuse 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. Likewise conceivable are embodiments in which the indentation is designed as a tab. In this case, a slot deviating from a straight line is introduced into the guide housing, which forms a tab connected to the guide housing. 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.
Das Trennelement kann beispielsweise als topfförmiger Kolben mit einem Bo- den und einem sich daran anschließenden Mantelabschnitt ausgebildet sein, wobei das Federelement an dem Boden anliegt. Vorteilhafterweise sind das Führungsgehäuse und der Kolben spanlos aus jeweils einem Blechrohling, beispielsweise mittels eines Tiefziehverfahrens, hergestellt. Der Boden des Kolbens dient als Druckfläche, die von dem einströmenden Druckmittel mit ei- ner 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. The separating element can be designed, for example, as a cup-shaped piston with a base and a jacket section adjoining it, the spring element resting against the base. 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. 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 Vorratsraums opposite the complementary space on a tight toleranced clearance between the shell portion and the inner circumferential surface of the guide housing.
Kurze Beschreibung der Zeichnungen Brief 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: 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:
Figur 1 nur sehr schematisch eine Brennkraftmaschine, FIG. 1 shows very schematically an internal combustion engine,
Figur 2 einen Längsschnitt durch einen Nockenwellenversteller, der an einer Nockenwelle befestigt ist, in der eine erste Ausführungsform eines Volumenspeichers angeordnet ist, 2 shows a longitudinal section through a camshaft adjuster, which is fastened to a camshaft, in which a first embodiment of a volume accumulator is arranged, FIG.
Figur 3 einen Querschnitt durch den Nockenwellenversteller aus Figur 2 entlang der Linie III-III, wobei die Zentralschraube nicht dargestellt ist, 3 shows a cross section through the camshaft adjuster from FIG. 2 along the line III-III, the central screw not being shown, FIG.
Figur 4 die Einzelheit X aus Figur 2 ohne Nockenwelle, FIG. 4 shows detail X from FIG. 2 without camshaft,
Figur 5 einen Querschnitt durch den Volumenspeicher entlang der Linie Figure 5 shows a cross section through the volume storage along the line
V-V in Figur 4,  V-V in FIG. 4,
Figur 6 einen perspektivische Ansicht der ersten Ausführungsform eines Figure 6 is a perspective view of the first embodiment of a
Volumenspeichers,  Volume reservoir,
Figur 7 einen perspektivische Ansicht einer zweiten Ausführungsform eines Volumenspeichers. Figure 7 is a perspective view of a second embodiment of a volume memory.
Ausführliche Beschreibung der Zeichnungen 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 1 1 für eine Relativdrehung zwischen der Kurbelwelle 2 und den Nockenwellen 6, 7 sorgen können. Nocken 8 der Nockenwellen 6, 7 betätigen ein oder mehrere Einlassgaswechsel- ventile 9 bzw. ein oder mehrere Auslassgaswechselventile 10. Ebenso kann vorgesehen sein nur eine der Nockenwellen 6, 7 mit einem Nockenwellenvers- teller 1 1 auszustatten, oder nur eine Nockenwelle 6, 7 vorzusehen, welche mit einem Nockenwellenversteller 1 1 versehen ist. Detailed description of the drawings 1 shows 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, wherein a first and a second camshaft adjuster 1 1 for 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 exhaust gas exchange valves 10. Equally, it may be provided only one of the camshafts 6, 7 with a Nockenwellenvers- teller 1 1, or only a camshaft 6, 7 provide, which is provided with a camshaft adjuster 1 1.
Die Figuren 2 und 3 zeigen einen Nockenwellenversteller 1 1 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 1 1 verbunden ist. Figures 2 and 3 show a camshaft adjuster 1 1 in the longitudinal or in the cross section. In addition, Figure 2 shows a volume accumulator 15 which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 1 1.
Der Nockenwellenversteller 1 1 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 ei- nes 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.  The camshaft adjuster 1 1 comprises 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 driven element 16 is designed in the form of an impeller and has a substantially cylindrical hub element 19, from the outer cylindrical surface of which in the illustrated embodiment, five wings 20 extend in the radial direction to the outside.
Innerhalb des Nockenwellenverstellers 1 1 sind fünf Druckräume 22 vorgese- hen, 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.  Within the camshaft adjuster 1 1, 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
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. 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. 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 No- ckenwellenverstellers 1 1 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. 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. 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. 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. 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, a pressure medium path 29 is formed, which communicates on the one hand with the openings 28 and on the other hand with a control valve 27 which serves to supply the camshaft adjuster 1 1 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. 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 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. 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.
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 ausge- miger 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 ange- passt, dass das Führungsgehäuse 33 druckmitteldicht in einen Vorratsraum 45 axial vor und einen Komplementärraum 46 hinter dem Boden 25 des Trennelements 34 getrennt wird. In the interior of the guide housing 33, the separating element 34 is arranged to be axially displaceable, wherein in the illustrated embodiment this is designed as a cup-shaped piston with a bottom 25 and a jacket section 26. miger piston with a bottom 25 and a skirt portion 26 is formed. 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.
Das Federelement 35 stützt sich einerseits an einem Federlager 39 (Figur 4), das an dem dem Nockenwellenversteller 1 1 abgewandten Ende des Führungs- gehäuses 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 wird durch drei radiale Einbuchtung 47 des Führungsgehäuses 33 ausgebildet, die in dieses hineinragen. Zu diesem Zweck sind in das zylindrische Führungs- gehäuse 33 drei erste Schlitze 40 eingebracht, die in Umfangsrichtung des Führungsgehäuses 33 verlaufen und in Umfangsrichtung beabstandet sind. Anschließend wird das Führungsgehäuse 33 in den Bereichen zwischen den ersten Schlitzen 40 und dem nockenwellenabgewandten Ende radial nach innen verformt. Die Tiefe der Einbuchtungen 47 ist so gewählt, dass das Feder- element 35 selbst bei maximaler Federexzentrizität an den offenen Enden, die durch die ersten Schlitze 40 von dem Führungsgehäuse 33 getrennt wurden, der Einbuchtungen 47 anliegt. Somit ist das Federlager 39 einteilig mit dem Führungsgehäuse 33 ausgebildet, wodurch die Herstellungskosten und der Herstellungsaufwand sinken.  The spring element 35 is supported on the one hand on a spring bearing 39 (FIG. 4), which is formed on the end of the guide housing 33 remote from the camshaft adjuster 11, and on the other hand on the bottom 25 of the separating element 34. 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 by three radial recess 47 of the guide housing 33, which project into this. For this purpose, 33 three first slots 40 are inserted into the cylindrical guide housing, which extend in the circumferential direction of the guide housing 33 and are spaced in the circumferential direction. Subsequently, the guide housing 33 is deformed radially inwardly in the areas between the first slots 40 and the end remote from the camshaft. The depth of the recesses 47 is selected so that the spring element 35 abuts the indentations 47 even at maximum spring eccentricity at the open ends which have been separated from the guide housing 33 by the first slots 40. Thus, the spring bearing 39 is formed integrally with the guide housing 33, whereby the manufacturing cost and the manufacturing cost decrease.
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 Herstel- lung 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. 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 stop is made 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 project 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 indentations 41 are produced 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.
Jede Einbuchtung 41 ragt derart in das Führungsgehäuse 33 hinein, dass deren offenes 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. Each indentation 41 protrudes into the guide housing 33 in such a way that its 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 section 43 which extends in the axial direction and runs parallel to the axis of the spring element 35. 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 einer alternativen Ausführungsform eines Volumenspeichers 15 beschreibt der erste Schlitz 40 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 L-förmigen zweiten Schlitz 40 eine rechteckige Lasche 44 ausgebildet, welche in das Führungsgehäuse 33 hineinragt. Dabei verläuft ein Abschnitt des L-förmigen Schlitzes 40 in Umfangsrich- tung des Führungsgehäuses 33, so dass das dadurch gebildete offene Ende als Federlager 39 dient. Der zweite Abschnitt des L-förmigen Schlitzes 40 er- streckt sich bis zum Ende des Führungsgehäuses 33. 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 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 an alternative embodiment of a volume memory 15, the first slot 40 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 shown in Figure 7 in a perspective view. In this embodiment, a rectangular tab 44 is formed by an L-shaped second slot 40, which projects into the guide housing 33. In this case, a portion of the L-shaped slot 40 extends in the circumferential direction of the guide housing 33, so that the open end formed thereby serves as a spring bearing 39. The second portion of the L-shaped slot 40 extends to the end of the guide housing 33. In addition to the embodiment shown in Figure 7, 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 in the axial direction in the guide housing 33 passes.
Bezugszeichen reference numeral
1 Brennkraftmaschine1 internal combustion engine
2 Kurbelwelle 2 crankshaft
3 Kolben  3 pistons
4 Zylinder  4 cylinders
5 Zugmitteltrieb  5 traction drive
6 Einlassnockenwelle 6 intake camshaft
7 Auslassnockenwelle7 exhaust camshaft
8 Nocken 8 cams
9 Einlassgaswechselventil 9 inlet gas exchange valve
10 Auslassgaswechselventil10 outlet gas exchange valve
1 1 Nockenwellenversteller1 1 Camshaft adjuster
12 Kettenrad 12 sprocket
13 Zentralschraube  13 central screw
14 Antriebselement  14 drive element
15 Volumenspeicher 15 volume memory
16 Abtriebselement 16 output element
17 Seitendeckel  17 side covers
18 Seitendeckel  18 side covers
19 Nabenelement  19 hub element
20 Flügel  20 wings
21 Umfangswand  21 peripheral wall
22 Druckraum  22 pressure chamber
23 erste Druckkammer 23 first pressure chamber
24 zweite Druckkammer24 second pressure chamber
25 Boden 25 floor
26 Mantelabschnitt  26 jacket section
27 Steuerventil  27 control valve
28 Öffnungen  28 openings
29 Druckmittelpfad 30 Druckmittelkanal29 pressure medium path 30 pressure medium channel
31 Hohlraum 31 cavity
32 Nockenwellenlager 32 camshaft bearings
33 Führungsgehäuse33 guide housing
34 Trennelement34 separating element
35 Federelement35 spring element
36 Wandung 36 wall
37 Druckmittelpumpe 37 pressure medium pump
38 Gehäuseöffnung38 housing opening
39 Federlager39 spring bearing
40 erster Schlitz40 first slot
41 Einbuchtung41 indentation
42 zweiter Schlitz42 second slot
43 Führungsabschnitt43 guiding section
44 Lasche 44 tab
45 Vorratsraum 45 pantry
46 Komplementärraum46 Complementary space
47 Einbuchtung 47 indentation
L Länge L length

Claims

1 1
Patentansprüche claims
Volumenspeicher (15) mit einem Führungsgehäuse (33), einem Trennelement (34) und einem Federelement (35), wobei das Trennelement (34) an einer Inneren Mantelfläche des Führungsgehäuses (33) verschiebbar gelagert ist und das Federelement (35) einerseits an dem Trennelement (34) und andererseits an dem Führungsgehäuse (33) anliegt, Volume memory (15) with a guide housing (33), a separating element (34) and a spring element (35), wherein the separating element (34) is displaceably mounted on an inner circumferential surface of the guide housing (33) and the spring element (35) on the one hand Separating element (34) and on the other hand against the guide housing (33),
dadurch gekennzeichnet, dass an dem Führungsgehäuse (33) zumindest eine Einbuchtung (47) ausgebildet ist, die in das Führungsgehäuse (33) hineinragt, wobei die Einbuchtung (47) in Richtung des Federelements (35) ein offenes Ende aufweist, an dem das Federelement (35) anliegt. characterized in that on the guide housing (33) at least one indentation (47) is formed, which projects into the guide housing (33), wherein the indentation (47) in the direction of the spring element (35) has an open end, on which the spring element (35) is present.
Volumenspeicher (15) nach Anspruch 1 , dadurch gekennzeichnet, dass die Einbuchtung (47) als Lasche (44) ausgebildet ist. Volume memory (15) according to claim 1, characterized in that the indentation (47) as a tab (44) is formed.
EP10773600.1A 2009-10-15 2010-10-14 Volume accumulator Not-in-force EP2488730B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049461A DE102009049461A1 (en) 2009-10-15 2009-10-15 volume storage
PCT/EP2010/065400 WO2011045368A1 (en) 2009-10-15 2010-10-14 Volume accumulator

Publications (2)

Publication Number Publication Date
EP2488730A1 true EP2488730A1 (en) 2012-08-22
EP2488730B1 EP2488730B1 (en) 2013-12-11

Family

ID=43417082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10773600.1A Not-in-force EP2488730B1 (en) 2009-10-15 2010-10-14 Volume accumulator

Country Status (5)

Country Link
US (1) US20120199231A1 (en)
EP (1) EP2488730B1 (en)
CN (1) CN102575535B (en)
DE (1) DE102009049461A1 (en)
WO (1) WO2011045368A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011075537A1 (en) * 2011-05-10 2012-11-15 Schaeffler Technologies AG & Co. KG Reciprocating internal combustion engine with camshaft adjusting device
DE102012218802B4 (en) * 2012-10-16 2018-05-17 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster system
CN109373037B (en) * 2018-11-14 2024-03-26 宁波太平洋电控系统有限公司 Central valve sleeve with camshaft lubricating structure

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GB8430562D0 (en) * 1984-12-04 1985-01-09 Carpenter & Paterson Ltd Spring support 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
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
EP0806550B2 (en) 1996-03-28 2008-08-20 Aisin Seiki Kabushiki Kaisha Valve timing control device
US5996632A (en) * 1998-12-14 1999-12-07 Aeroquip Corporation Pressure relief adapter
US6782856B2 (en) * 2002-04-09 2004-08-31 Ford Global Technologies, Llc Camshaft accumulator
WO2008140897A1 (en) * 2007-05-14 2008-11-20 Borgwarner Inc. Cam mounted accumulator
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

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Also Published As

Publication number Publication date
DE102009049461A1 (en) 2011-04-21
WO2011045368A1 (en) 2011-04-21
US20120199231A1 (en) 2012-08-09
CN102575535B (en) 2014-07-02
CN102575535A (en) 2012-07-11
EP2488730B1 (en) 2013-12-11

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