EP1073830B1 - Camshaft adjuster for internal combustion engines - Google Patents

Camshaft adjuster for internal combustion engines Download PDF

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Publication number
EP1073830B1
EP1073830B1 EP99916918A EP99916918A EP1073830B1 EP 1073830 B1 EP1073830 B1 EP 1073830B1 EP 99916918 A EP99916918 A EP 99916918A EP 99916918 A EP99916918 A EP 99916918A EP 1073830 B1 EP1073830 B1 EP 1073830B1
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EP
European Patent Office
Prior art keywords
camshaft
inner body
relation
outer body
camshaft adjuster
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.)
Expired - Lifetime
Application number
EP99916918A
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German (de)
French (fr)
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EP1073830A1 (en
Inventor
Wolfgang Speier
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.)
Daimler AG
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DaimlerChrysler AG
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Publication of EP1073830A1 publication Critical patent/EP1073830A1/en
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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
    • 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
    • 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
    • F01L2001/3443—Solenoid driven oil control valves
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a camshaft adjuster for internal combustion engines according to the preamble of claim 1.
  • Camshaft adjusters are available as piston adjusters with axially displaceable Pistons (DE 40 29 849 C2, DE 196 11 365 A1 and DE 197 26 300 A1, Figure 1) as well as a wing adjuster with in Wings that can be acted upon and pivoted in the circumferential direction (DE 197 26 300 A1, Figures 7 to 10) known.
  • the Camshaft adjuster in front extension of the camshaft via a central clamping screw.
  • the camshaft is non-rotatable Inner body of the camshaft adjuster and its opposite the inner body rotatable over which the Drive connection to the crankshaft runs, on the clamping screw to lead, regardless of an independent centering of the inner body opposite the camshaft.
  • This requires very tight tolerances, i.e. high manufacturing costs, and also leads through the overlay of several games radial guides to misalignment errors that affect the Impact concentricity and the vibration behavior can, such concentricity and misalignment errors there also make it difficult to control the spool over the housing side assigned, axially offset actuating magnet as an actuator with the smallest possible gap dimension from the spool operated anchor. Lead larger gaps but to increased power requirements and thus increased space requirements, considering the structural conditions of internal combustion engines for motor vehicles with regard to axial extension due to the camshaft adjuster is often unavailable.
  • the invention is intended to provide a camshaft adjuster at the beginning be mentioned in such a way that a centering of the camshaft adjuster as good as possible through which the requirements for created a particularly simple and inexpensive production become.
  • the invention Design with centering of the entire camshaft adjuster, including connecting the through the multi-way valve formed control device to the actuator, Particularly favorable conditions via the clamping screw for a largely tolerance-free centering without Excessive manufacturing requirements, with the best prerequisites for the best possible and vibration-free Concentricity and with the smallest possible required gap dimensions in the transition between control spool and actuator.
  • the camshaft adjuster according to Figures 1 to 3 is a total designated 1 and in association with a camshaft 2 one Internal combustion engine 3 shown here only in its outline is indicated and at the end of the camshaft shown 2 associated end face a chain case 4 is provided is essentially only shown in its outline is. On this chain case 4 is in an axial extension Camshaft 2, and this opposite, the camshaft adjuster 1 assigned actuator 5 is provided, the is formed by a solenoid and from the outside the end face of the internal combustion engine 3 Chain case 4 is screwed on, as indicated at 5.
  • the actuator 5 formed by an actuating magnet acts with the armature 7 of a spool 8 together in a Central screw is integrated as a clamping screw 9, via the the camshaft adjuster 1 on the front of the camshaft 2 is flanged, the clamping screw 9 with the control slide 8 of the camshaft adjuster 1 and the actuator 5 is coaxial with the camshaft 2.
  • the outer body 111 has a radial distribution over its circumference inwardly projecting piston wings 13 on the part of the inner body 110 counter wings 14 are assigned, each two counter wings 14 delimit a ring sector 15 in which a Piston wing 13 of the outer body 111 lies, the outer body 111 with its piston wings 13 assigned to it, so to speak Vane rotor forms over the inner body 110 an angular range is adjustable by the counter wing 14 of a ring sector 15 is limited.
  • Piston vanes delimit within the respective ring sector 15 13 and counter wing 14 each two working chambers 16, 17, the are hydraulically acted upon, controlled by the Control spool 8.
  • the supply of pressure medium to the respective working chamber 16 and 17 is carried out in a manner not shown via a Bearing point of the camshaft 2 in the housing of the internal combustion engine and radial bores 20 in the camshaft 2.
  • the annular collar 26 remote from the camshaft 2 also limits another, after the side remote from the camshaft 2 offset ring collar 28 a further annular space 29, the a radial connection bore and an axial bore 30 with the Receptacle 31 is connected via a the bottom side Limitation of the receptacle 31 through bore 32 and one radial, penetrating the centering collar 119 of the camshaft 2 Connection channel 33 opens into the chain case 4.
  • the ring sectors containing the working chambers 16 and 17 are closed axially by the ring covers 134 and 135, the parts of the end faces of the inner body 110 and the outer body 111 cover and which over axial clamping screws 38 against the flat end faces of the inner body 110 and the Outer body 111 are held adjacent.
  • a locking element 39 is provided in the form of a radial bolt, the spring-loaded towards the inner body 110 and which is assigned a detent opening 40 in the inner body 110 is.
  • the latching opening 40 overlaps one the radial channel 41 opening out of the chamber 16, of an inner circumference of the inner body 110 provided annular groove 42.
  • This annular groove 42 overlaps radial bores 43 in the guide forming the control slide 8, the recording 31 for the control slide 8 limiting axial wall Tensioning screw 9.
  • the radial bore 20 supplied in the camshaft 2 pressure medium, the via the axial channels 21 and 22 into the annular space 25 of the control slide 8 arrives.
  • the blocking element 39 is thereby shifted against the spring force, which over the Locking element 39 exercised locking and the outer body 111, based on the representation according to Figure 2 in a counterclockwise direction towards an early position of the camshaft 2 pivoted.
  • the solenoid 5 as continuous controlling element, for example as a proportional magnet adjusted accordingly, i.e. by supply or Draining pressure medium to one or the other chamber 16 or 17 made the necessary adjustment.
  • control slide goes 8 back to the starting position shown, in which the chamber 16 is connected to the return via the annular space 29, so that the chamber 16 empties and at the same time the the locking element 39 forming bolts by the spring force in its locked position can be moved.
  • both end positions of the control slide 8 is the one that is not pressurized in each case Chamber open against the return.

Abstract

According to the invention, a camshaft adjuster (1) for internal combustion engines is constructed with a central tensioning screw (9) for fixing said adjuster (1) in relation to a camshaft (2), the slide (8) for controlling the supply of the pressure medium to the camshaft adjuster (1) being integrated into said tensioning screw (9). The tensioning screw (9) forms the mounting of the camshaft adjuster (1), directly centring and fixing said camshaft adjuster (1) in relation to the camshaft (2).

Description

Die Erfindung betrifft einen Nockenwellenversteller für Brennkraftmaschinen gemäß dem Oberbegriff des Anspruches 1.The invention relates to a camshaft adjuster for internal combustion engines according to the preamble of claim 1.

Nockenwellenversteller sind als Kolbenversteller mit axial verschiebbarem Kolben (DE 40 29 849 C2, DE 196 11 365 A1 und DE 197 26 300 A1, Figur 1) wie auch als Flügelversteller mit in Umfangsrichtung beaufschlagbaren und verschwenkbaren Flügeln (DE 197 26 300 A1, Figuren 7 bis 10) bekannt.Camshaft adjusters are available as piston adjusters with axially displaceable Pistons (DE 40 29 849 C2, DE 196 11 365 A1 and DE 197 26 300 A1, Figure 1) as well as a wing adjuster with in Wings that can be acted upon and pivoted in the circumferential direction (DE 197 26 300 A1, Figures 7 to 10) known.

In Verbindung mit beiden Bauformen erfolgt die Befestigung des Nockenwellenverstellers in stirnseitiger Verlängerung der Nokkenwelle über eine zentrale Spannschraube.In connection with both designs, the Camshaft adjuster in front extension of the camshaft via a central clamping screw.

Zur Steuerung der hydraulischen Druckversorgung -des Nockenwellenverstellers ist es aus der DE 40 29 849 C2 bekannt, ein externes 4/2 Wegeventil vorzusehen, von dem aus Versorgungskanäle zur Nockenwelle und zu dem hier als Stellmittel vorgesehenen Stellkolben verlaufen, der in einem Aufnahmeraum zwischen Innen- und Außenkörper angeordnet ist, wobei über den Außenkörper die Antriebsverbindung zur Kurbelwelle verläuft. To control the hydraulic pressure supply of the camshaft adjuster it is known from DE 40 29 849 C2, an external one 4/2 way valve to be provided, from which supply channels to the camshaft and to the one provided here as adjusting means Actuating piston run, which in a receiving space between indoor and the outer body is arranged, with the outer body the drive connection to the crankshaft runs.

Dadurch bedingte lange Leitungswege mit der Gefahr entsprechender Leckagen sowie auch gewisser Elastizitäten können dazu führen, dass das System eine hydraulisch ungenügende Steifigkeit aufweist und damit eine zufriedenstellende Regelung erschwert, ungeachtet dessen, dass die externe Anordnung der durch das Wegeventil gebildeten Steuereinrichtung den Bauaufwand und die Größe des erforderlichen Bauraumes negativ beeinflusst.As a result, long cable routes with the corresponding risk Leakages as well as certain elasticities can do this cause the system to have a hydraulically insufficient rigidity and thus complicates a satisfactory regulation, notwithstanding that the external arrangement of the control means formed by the directional control valve the construction effort and negatively affects the size of the installation space required.

Durch die DE 196 11 365 A1, die im Oberbegriff des Anspruches 1 berücksichtigt ist, ist es darüber hinaus bekannt, die als Mehrwegeventil ausgebildete Steuereinrichtung in die Spannschraube zu integrieren, so dass diese als Gehäuse eine axiale Aufnahme für einen zentral liegenden und axial verschiebbaren Steuerschieber bildet, über den radial auf kurzen Wegen die Druckmittelversorgung der Stellmittel erfolgen kann.By DE 196 11 365 A1, which is in the preamble of the claim 1 is considered, it is also known as Multi-way valve trained control device in the clamping screw to integrate, so that this as an axial housing Holder for a centrally located and axially displaceable Control spool forms the radial over the short ways Pressure medium supply to the actuating means can take place.

Im Hinblick hierauf ist vorgesehen, den zur Nockenwelle drehfesten Innenkörper des Nockenwellenverstellers und dessen gegenüber dem Innenkörper verdrehbaren Außenkörper, über den die Antriebsverbindung zur Kurbelwelle läuft, auf der Spannschraube zu führen, ungeachtet einer hiervon unabhängigen Zentrierung des Innenkörpers gegenüber der Nockenwelle. Dies bedingt sehr enge Tolerierungen, also hohen Fertigungsaufwand, und führt zudem durch die Überlagerung mehrerer spielbehafteter radialer Führungen zu Desachsierungsfehlern, die sich auf den Rundlauf und das Schwingungsverhalten nachteilig auswirken können, wobei solche Rundlauf- und Desachsierungsfehler es auch erschweren, den Steuerschieber über den diesem gehäuseseitig zugeordneten, axial versetzten Stellmagneten als Stellantrieb bei möglichst geringem Spaltmaß zum vom Steuerschieber getragenen Anker zu betreiben. Größere Spaltmaße führen aber zu erhöhtem Leistungsbedarf und damit erhöhtem Raumbedarf, der in Anbetracht der baulichen Gegebenheiten bei Brennkraftmaschinen für Kraftfahrzeuge schon im Hinblick auf die durch den Nockenwellenversteller bedingte axiale Verlängerung häufig nicht zur Verfügung steht. In view of this, it is provided that the camshaft is non-rotatable Inner body of the camshaft adjuster and its opposite the inner body rotatable over which the Drive connection to the crankshaft runs, on the clamping screw to lead, regardless of an independent centering of the inner body opposite the camshaft. This requires very tight tolerances, i.e. high manufacturing costs, and also leads through the overlay of several games radial guides to misalignment errors that affect the Impact concentricity and the vibration behavior can, such concentricity and misalignment errors there also make it difficult to control the spool over the housing side assigned, axially offset actuating magnet as an actuator with the smallest possible gap dimension from the spool operated anchor. Lead larger gaps but to increased power requirements and thus increased space requirements, considering the structural conditions of internal combustion engines for motor vehicles with regard to axial extension due to the camshaft adjuster is often unavailable.

Durch die Erfindung soll ein Nockenwellenversteller der eingangs genannten Art dahingehend ausgebildet werden, dass eine möglichst gute Zentrierung des Nockenwellenverstellers erreicht wird, durch die gleichzeitig die Voraussetzungen für eine besonders einfache und preisgünstige Fertigung geschaffen werden.The invention is intended to provide a camshaft adjuster at the beginning be mentioned in such a way that a centering of the camshaft adjuster as good as possible through which the requirements for created a particularly simple and inexpensive production become.

Gemäß der Erfindung wird dies durch die Merkmale des Anspruches 1 erreicht, denen zufolge die Spannschraube das gegenüber der Nockenwelle zentrierende Element des Nockenwellenverstellers bildet, so dass dieser bezüglich seines Innen- und Außenkörpers sowie auch seiner seitlichen Abschlusselemente in Form von Deckeln keine zusätzliche zentrierende Abstützung benötigt. Damit entfällt die Notwendigkeit von axialen Hinterschneidungen oder Vorsprüngen an Innen- und Außenkörper, die die Fertigung erschweren, und es wird möglich, den Nockenwellenversteller als Flügelsteller mit scheibenförmigem Innenkörper und Außenkörper sowie scheibenförmigen Deckeln aufzubauen. Für die Deckel erweist sich eine lediglich axiale Verspannung gegeneinander bzw. gegen den Außenkörper als ausreichend, was zu einer weiteren Vereinfachung führt. Zudem ergibt die erfindungsgemäße Ausgestaltung mit Zentrierung des gesamten Nockenwellenverstellers, einschließlich des Anschlusses der durch das Mehrwegeventil gebildeten Steuereinrichtung an den Stellantrieb, über die Spannschraube besonders günstige Voraussetzungen für eine weitgehend toleranzfreie Zentrierung ohne übermäßige Anforderungen an die Fertigung, mit besten Voraussetzungen für einen möglichst guten und schwingungsfreien Rundlauf sowie mit möglichst geringen, erforderlichen Spaltmaßen im Übergang zwischen Steuerschieber und Stellantrieb.According to the invention this is through the features of the claim 1 reached, according to which the tension screw opposite the camshaft centering element of the camshaft adjuster forms, so that this with respect to its inner and outer body as well as its side end elements in shape no additional centering support is required for lids. This eliminates the need for axial undercuts or protrusions on the inner and outer body that complicate the manufacture, and it becomes possible to adjust the camshaft adjuster as a wing adjuster with a disc-shaped inner body and outer body and disc-shaped lids. Only an axial bracing has been found for the cover against each other or against the outer body as sufficient what leads to further simplification. In addition, the invention Design with centering of the entire camshaft adjuster, including connecting the through the multi-way valve formed control device to the actuator, Particularly favorable conditions via the clamping screw for a largely tolerance-free centering without Excessive manufacturing requirements, with the best prerequisites for the best possible and vibration-free Concentricity and with the smallest possible required gap dimensions in the transition between control spool and actuator.

Als zweckmäßig erweist es sich, wenn die Deckel radial innen an den Zentrierbund der Nockenwelle anschließen, so dass eine ausreichende radiale Überdeckung zu Innen- und Außenkörper gegeben ist, die die Verwendung einfacher Dichtmittel möglich macht, sofern solche vorgesehen werden sollen, wobei die durch die Erfindung erreichte exakte Zentrierung mit geringen Spielen sich auch im Hinblick auf die Reduzierung von Leckagen günstig auswirkt.It proves expedient if the cover is located radially on the inside connect to the centering collar of the camshaft so that a sufficient radial overlap is given to the inner and outer body is that the use of simple sealants is possible makes, if such should be provided, the by the invention achieved exact centering with little play also in terms of reducing leakage has a favorable effect.

Weitere Einzelheiten und. Merkmale der Erfindung ergeben sich aus den Ansprüchen. Desweiteren wird die Erfindung anhand der Zeichnungen mit zusätzlichen Einzelheiten erläutert. Es zeigen:

Fig. 1
in einer Schnittdarstellung gemäß Linie I-I in Fig. 2 einen Längsschnitt durch einen Nockenwellenversteller gemäß der Erfindung, teilweise schematisiert dargestellt, wobei der Nockenwellenversteller in Verlängerung zur Nockenwelle der in Einzelheiten nicht dargestellten Brennkraftmaschine angeordnet ist und von einem ebenfalls nur in seinen Umrissen angedeuteten, stirnseitig zur Brennkraftmaschine vorgesehenen Kettenkasten aufgenommen wird,
Fig. 2
einen Schnitt gemäß Linie II-II in Figur 1, in vereinfachter Darstellung, und
Fig. 3
eine weitgehend entsprechende, vergrößerte Darstellung des zentralen, den Steuerschieber umfassenden Bereiches des Nockenwellenverstellers gemäß Figur 1.
More details and. Features of the invention result from the claims. Furthermore, the invention is explained with additional details with reference to the drawings. Show it:
Fig. 1
in a sectional view along line II in Fig. 2 shows a longitudinal section through a camshaft adjuster according to the invention, partially shown schematically, the camshaft adjuster is arranged in extension to the camshaft of the internal combustion engine, not shown in detail, and by a front side also indicated only in its outline Internal combustion engine provided chain case is added
Fig. 2
a section along line II-II in Figure 1, in a simplified representation, and
Fig. 3
a largely corresponding, enlarged representation of the central area of the camshaft adjuster comprising the control slide according to FIG. 1.

Der Nockenwellenversteller gemäß Figuren 1 bis 3 ist insgesamt mit 1 bezeichnet und in Zuordnung zu einer Nockenwelle 2 einer Brennkraftmaschine 3 dargestellt, die hier nur in ihren Umrissen angedeutet ist únd an deren dem dargestellten Ende der Nokkenwelle 2 zugeordneter Stirnseite ein Kettenkasten 4 vorgesehen ist, der im wesentlichen nur in seinen Umrissen dargestellt ist. An diesem Kettenkasten 4 ist in axialer Verlängerung zur Nockenwelle 2, und dieser gegenüberliegend, der dem Nockenwellenversteller 1 zugeordnete Stellantrieb 5 vorgesehen, der durch einen Stellmagneten gebildet ist und der von außen auf die der Brennkraftmaschine 3 gegenüberliegende Stirnseite des Kettenkastens 4 aufgeschraubt ist, wie bei 5 angedeutet.The camshaft adjuster according to Figures 1 to 3 is a total designated 1 and in association with a camshaft 2 one Internal combustion engine 3 shown here only in its outline is indicated and at the end of the camshaft shown 2 associated end face a chain case 4 is provided is essentially only shown in its outline is. On this chain case 4 is in an axial extension Camshaft 2, and this opposite, the camshaft adjuster 1 assigned actuator 5 is provided, the is formed by a solenoid and from the outside the end face of the internal combustion engine 3 Chain case 4 is screwed on, as indicated at 5.

Der durch einen Stellmagneten gebildete Stellantrieb 5 wirkt mit dem Anker 7 eines Steuerschiebers 8 zusammen, der in eine Zentralschraube als Spannschraube 9 integriert ist, über die der Nockenwellenversteller 1 stirnseitig an der Nockenwelle 2 angeflanscht ist, wobei die Spannschraube 9 mit dem Steuerschieber 8 des Nockenwellenverstellers 1 sowie dem Stellantrieb 5 koaxial zur Nockenwelle 2 liegt.The actuator 5 formed by an actuating magnet acts with the armature 7 of a spool 8 together in a Central screw is integrated as a clamping screw 9, via the the camshaft adjuster 1 on the front of the camshaft 2 is flanged, the clamping screw 9 with the control slide 8 of the camshaft adjuster 1 and the actuator 5 is coaxial with the camshaft 2.

Auf der Spannschraube 9 sitzt, gegen die Nockenwelle 2 axial verspannt, der Innenkörper 110 des Nockenwellenverstellers 1, dem ein Außenkörper 111 zugeordnet ist, der an seinem Außenumfang Verzahnungen 12 aufweist, über die, in fester Zuordnung in Bezug auf Drehrichtung und Drehzahl, die Nockenwelle 2 von der hier nicht dargestellten Kurbelwelle der Brennkraftmaschine 3 angetrieben wird. Anstelle eines hier angesprochenen und angedeuteten Kettentriebes können selbstverständlich auch andere Antriebsverbindungen treten, wie beispielsweise Zahnriementriebe oder auch Zahnradtriebe.Sitting on the clamping screw 9 axially against the camshaft 2 clamped, the inner body 110 of the camshaft adjuster 1, which is assigned an outer body 111, on its outer circumference Gears 12, on which, in a fixed assignment in Regarding direction of rotation and speed, the camshaft 2 from the Crankshaft of internal combustion engine 3, not shown here is driven. Instead of one that was mentioned and suggested here Of course, chain drives can also do other things Drive connections occur, such as toothed belt drives or also gear drives.

Der Außenkörper 111 weist über seinen Umfang verteilt radial nach innen ragende Kolbenflügel 13 auf, denen seitens des Innenkörpers 110 Gegenflügel 14 zugeordnet sind, wobei jeweils zwei Gegenflügel 14 einen Ringsektor 15 begrenzen, in dem ein Kolbenflügel 13 des Außenkörpers 111 liegt, wobei der Außenkörper 111 mit seinen ihm zugeordneten Kolbenflügeln 13 quasi einen Flügelrotor bildet, der gegenüber dem Innenkörper 110 über einen Winkelbereich verstellbar ist, der durch die Gegenflügel 14 eines Ringsektors 15 begrenzt ist.The outer body 111 has a radial distribution over its circumference inwardly projecting piston wings 13 on the part of the inner body 110 counter wings 14 are assigned, each two counter wings 14 delimit a ring sector 15 in which a Piston wing 13 of the outer body 111 lies, the outer body 111 with its piston wings 13 assigned to it, so to speak Vane rotor forms over the inner body 110 an angular range is adjustable by the counter wing 14 of a ring sector 15 is limited.

Innerhalb des jeweiligen Ringsektors 15 begrenzen Kolbenflügel 13 und Gegenflügel 14 jeweils zwei Arbeiriskammern 16, 17, die hydraulisch beaufschlagbar sind, und zwar gesteuert über den Steuerschieber 8. Piston vanes delimit within the respective ring sector 15 13 and counter wing 14 each two working chambers 16, 17, the are hydraulically acted upon, controlled by the Control spool 8.

Aus Figuren 1 und 3 ist ersichtlich, daß die Zentrierung der Spannschraube 9 gegenüber der Nockenwelle 2 über einen Zentrierbund 119 der Nockenwelle 2 erfolgt, der sich unmittelbar gegen den Umfang der Spannschraube 9 abstützt. Diese Zentrierung zwischen Spannschraube 9 und Nockenwelle 2 im Bereich des der Nockenwelle 2 benachbarten Endbereiches macht es möglich, den Innenkörper 110 und den Außenkörper 111 als plane Scheiben auszubilden, so daß diese in zur Achse der Nockenwelle 2 senkrecht stehenden Ebenen liegende Stirnseiten aufweisen und durch ebenfalls plane, als Ringdeckel ausgebildete Deckel 134, 135 abgedeckt werden können. In Verbindung mit der axialen Verspannung der Spannschraube 9 gegenüber der Nockenwelle 2 ermöglicht der mit dem Umfang der Spannschraube 9 zusammenwirkende Zentrierbund 119 somit eine unmittelbare Ausrichtung der Spannschraube 9 auf die Nockenwelle 2, so daß sich bei einfacher Herstellung eine bezüglich der Passungsspiele gut beherrschbare Fertigung für den Nockenwellenversteller 1 ergibt. Dies gilt insbesondere auch in Bezug auf den Innenkörper 110 sowie den Außenkörper 111 und die diese axial überdeckenden Ringdeckel 134, 135, da diese Teile sämtlich zumindest bezüglich der zusammenwirkenden Flächen als plane Scheiben ausgebildet werden können, was bei einfacher Herstellung auch enge Toleranzen ermöglicht. Dies macht es gegebenenfalls auch möglich, die Deckel 134, 135 dichtungsfrei gegen Innenkörper 110 und Außenkörper 111 zu verspannen, obwohl sich Dichtungen, wie bei 147 dargestellt, als Ringdichtungen bei einer solchen Lösung ohne besonders großen Aufwand in die zusammenwirkenden Flächen einarbeiten lassen. Solche Abdichtungen sind im Regelfall aber auch deshalb entbehrlich, weil die Arbeitsdrücke verhältnismäßig niedrig sind und Leckagen im Rahmen der durch Planschliff möglichen Feinbearbeitung auch ohne Dichtungen auf ein Maß beschränkt sind, das bei Anordnung des Nockenwellenverstellers 1 im Kettenkasten 4 hingenommen werden kann.From Figures 1 and 3 it can be seen that the centering of the Tensioning screw 9 opposite the camshaft 2 via a centering collar 119 of the camshaft 2, which is immediate is supported against the circumference of the clamping screw 9. This centering between clamping screw 9 and camshaft 2 in the area of the camshaft 2 adjacent end region makes it possible the inner body 110 and the outer body 111 as flat disks form so that they are perpendicular to the axis of the camshaft 2 have standing end faces and standing through also flat covers 134, 135 designed as ring covers can be covered. In connection with the axial bracing of the clamping screw 9 relative to the camshaft 2 the centering collar cooperating with the circumference of the clamping screw 9 119 thus an immediate alignment of the clamping screw 9 on the camshaft 2, so that it is easier Production of a manageable with respect to the fit games Manufacturing for the camshaft adjuster 1 results. this applies in particular also with respect to the inner body 110 and the Outer body 111 and the ring cover axially covering these 134, 135, since all of these parts interact at least with regard to the Surfaces are formed as flat disks can, which allows tight tolerances with simple production. This may also make it possible for the cover 134, 135 seal-free against inner body 110 and outer body 111 tighten, although seals, as shown at 147, as ring seals in such a solution without special incorporate great effort into the interacting surfaces to let. Such seals are usually also therefore unnecessary because the working pressures are proportional are low and leakages are within the limits of surface grinding Finishing is limited to one size even without seals are, the arrangement of the camshaft adjuster 1 can be accepted in the chain case 4.

Die Zuführung von Druckmedium auf die jeweilige Arbeitskammer 16 bzw. 17 erfolgt in nicht näher dargestellter Weise über eine Lagerstelle der Nockenwelle 2 im Gehäuse der Brennkraftmaschine und Radialbohrungen 20 in der Nockenwelle 2. Ausgehend hiervon führt ein Axialkanal 21, 22 über Nockenwelle 2 und Innenkörper 110 zu einem Ringraum 23 im Innenkörper 110, der in Überdeckung zu Radialbohrungen 24 in der Spannschraube 9 liegt. Diese münden auf einen Ringraum 25 des Steuerschiebers 8 aus, der zwischen Ringbunden 26, 27 des Steuerschiebers 8 liegt, über die der Ringraum 25 axial begrenzt ist.The supply of pressure medium to the respective working chamber 16 and 17 is carried out in a manner not shown via a Bearing point of the camshaft 2 in the housing of the internal combustion engine and radial bores 20 in the camshaft 2. Starting from this leads an axial channel 21, 22 over camshaft 2 and inner body 110 to an annular space 23 in the inner body 110, which overlaps to radial bores 24 in the clamping screw 9. These lead to to an annular space 25 of the spool 8, which between Ring bundles 26, 27 of the control slide 8 is located on the the annular space 25 is axially limited.

Der von der Nockenwelle 2 abgelegene Ringbund 26 begrenzt mit einem weiteren, nach der von der Nockenwelle 2 abgelegenen Seite versetzten Ringbund 28 einen weiteren Ringraum 29, der über eine radiale Anschlußbohrung und eine Axialbohrung 30 mit der Aufnahme 31 in Verbindung steht, die über eine die bodenseitige Begrenzung der Aufnahme 31 durchsetzende Bohrung 32 und einen radialen, den Zentrierbund 119 der Nockenwelle 2 durchsetzenden Verbinduncskanal 33 in den Kettenkasten 4 ausmündet.The annular collar 26 remote from the camshaft 2 also limits another, after the side remote from the camshaft 2 offset ring collar 28 a further annular space 29, the a radial connection bore and an axial bore 30 with the Receptacle 31 is connected via a the bottom side Limitation of the receptacle 31 through bore 32 and one radial, penetrating the centering collar 119 of the camshaft 2 Connection channel 33 opens into the chain case 4.

Die die Arbeitskammern 16 und 17 beinhaltenden Ringsektoren sind axial durch die Ringdeckel 134 und 135 geschlossen, die flächig Teile der Stirnflächen des Innenkörpers 110 und des Außenkörpers 111 überdecken und welche über axiale Spannschrauben 38 gegen die planen Stirnflächen des Innenkörpers 110 und des Außenkörpers 111 anliegend gehalten sind. The ring sectors containing the working chambers 16 and 17 are closed axially by the ring covers 134 and 135, the parts of the end faces of the inner body 110 and the outer body 111 cover and which over axial clamping screws 38 against the flat end faces of the inner body 110 and the Outer body 111 are held adjacent.

Zur Fixierung des Außenkörpers 111 als Flügelrotor in seiner der Startstellung der Brennkraftmaschine entsprechenden Stellung, die im Regelfall einer Spät-Stellung der Nockenwelle 2 entspricht, ist im Bereich eines Kolbenflügels 13 des Außenkörpers 111 ein Sperrelement 39 in Form eines Radialbolzens vorgesehen, der in Richtung auf den Innenkörper 110 federbelastet ist und dem im Innenkörper 110 eine Rastöffnung 40 zugeordnet ist. Die Rastöffnung 40 steht in Überschneidung zu einem auf die Kammer 16 ausmündenden Radialkanal 41, der von einer im Innenumfang des Innenkörpers 110 vorgesehenen Ringnut 42 ausgeht. Diese Ringnut 42 steht in Überdeckung zu Radialbohrungen 43 in der die Führung des Steuerschiebers 8 bildenden, die Aufnahme 31 für den Steuerschieber 8 begrenzenden Axialwandung der Spannschraube 9. Bezogen auf die Darstellung gemäß Figur 1 axial versetzt und auf die jeweils andere Arbeitskammer 17 ausmündend sind, in Figur 2 strichliert dargestellt, Radialkanäle 44 im Innenkörper 110 vorgesehen, die auf Ringnuten 45 ausmünden, welche in Überdeckung zu Radialbohrungen 46 in der Wandung der Spannschraube 9 stehen.To fix the outer body 111 as a vane rotor in its position corresponding to the starting position of the internal combustion engine, which is usually a late position of the camshaft 2 is in the region of a piston wing 13 of the outer body 111 a locking element 39 is provided in the form of a radial bolt, the spring-loaded towards the inner body 110 and which is assigned a detent opening 40 in the inner body 110 is. The latching opening 40 overlaps one the radial channel 41 opening out of the chamber 16, of an inner circumference of the inner body 110 provided annular groove 42. This annular groove 42 overlaps radial bores 43 in the guide forming the control slide 8, the recording 31 for the control slide 8 limiting axial wall Tensioning screw 9. Based on the illustration according to FIG. 1 axially offset and merging with the other working chamber 17 are shown in dashed lines in Figure 2, radial channels 44 provided in the inner body 110, which open out on annular grooves 45, which overlap with radial bores 46 in the wall the clamping screw 9 are.

Wird die Brennkraftmaschine 3 angefahren, so wird über die Radialbohrung 20 in der Nockenwelle 2 Druckmedium zugeführt, das über die Axialkanäle 21 und 22 in den Ringraum 25 des Steuerschiebers 8 gelangt. Der Startstellung entsprechend nimmt dieser zunächst eine der Nockenwelle 2 benachbarte, federbelastete Endlage an, bis mit Durchführung des Startvorganges der Stellantrieb 5 aktiviert und durch den Stellmagneten der Anker 7 angezogen wird, so daß der Ringraum 25 in Überdeckung zur Radialbohrung 43 in der Spannschraube 9 und über die Ringnut 42 zum Radialkanal 41 kommt, und damit das Sperrelement 39 und die Kammer 16 mit Druckmedium beaufschlagt. Das Sperrelement 39 wird hierdurch entgegen der Federkraft verschoben, die über das Sperrelement 39 ausgeübte Verriegelung aufgehoben und der Außenkörper 111, bezogen auf die Darstellung gemäß Figur 2 im Gegenuhrzeigersinn in Richtung einer Früh-Stellung der Nockenwelle 2 verschwenkt. Ist über eine entsprechende Ansteuerung des Steuermagneten des Stellantriebes 5, in Abhängigkeit von der Motorsteuerung, die gewünschte Nockenwellenlage erreicht, so wird der Steuerschieber 8 mit seinen beiden Ringbunden 26 und 27 in Überdeckung zu den Bohrungen 43 und 46 gebracht, die Zufuhr von Druckmedium zu den Kammern 16 und 17 also unterbrochen, solange die angestrebte Sollage der Nockenwelle gegeben ist. Ergeben sich gegenüber dieser, beispielsweise durch Leckagen, Verschiebungen, so wird über den Stellmagneten 5 als kontinuierlich steuerndes Element, beispielsweise als Proportionalmagnet entsprechend nachgesteuert, also durch Zufuhr bzw. Ablassen von Druckmedium zu der einen oder anderen Kammer 16 bzw. 17 die notwendige Nachstellung vorgenommen.If the internal combustion engine 3 is started, the radial bore 20 supplied in the camshaft 2 pressure medium, the via the axial channels 21 and 22 into the annular space 25 of the control slide 8 arrives. This takes the starting position First, one of the camshaft 2 adjacent, spring-loaded End position until the actuator is started 5 activated and by the control magnet of the armature 7 is tightened so that the annular space 25 overlaps the radial bore 43 in the clamping screw 9 and over the annular groove 42 comes to the radial channel 41, and thus the locking element 39 and the Chamber 16 pressurized with pressure medium. The blocking element 39 is thereby shifted against the spring force, which over the Locking element 39 exercised locking and the outer body 111, based on the representation according to Figure 2 in a counterclockwise direction towards an early position of the camshaft 2 pivoted. Is a corresponding control of the Control magnets of the actuator 5, depending on the Engine control, the desired camshaft position reached, so the control slide 8 with its two ring bundles 26 and 27 brought into alignment with the holes 43 and 46, the feed interrupted by pressure medium to the chambers 16 and 17, as long as the desired target position of the camshaft is given is. Compared to this, for example due to leaks, Displacements, so the solenoid 5 as continuous controlling element, for example as a proportional magnet adjusted accordingly, i.e. by supply or Draining pressure medium to one or the other chamber 16 or 17 made the necessary adjustment.

Wird die Brennkraftmaschine 3 abgeschaltet, so geht der Steuerschieber 8 in die gezeigte Ausgangslage zurück, in der die Kammer 16 über den Ringraum 29 an den Rücklauf angeschlossen ist, so daß sich die Kammer 16 entleert und gleichzeitig auch der das Sperrelement 39 bildende Bolzen durch die Federkraft in seine Sperrstellung verschoben werden kann. In beiden Endstellungen des Steuerschiebers 8 ist die jeweils nicht druckbeaufschlagte Kammer gegen den Rücklauf offen. If the internal combustion engine 3 is switched off, the control slide goes 8 back to the starting position shown, in which the chamber 16 is connected to the return via the annular space 29, so that the chamber 16 empties and at the same time the the locking element 39 forming bolts by the spring force in its locked position can be moved. In both end positions of the control slide 8 is the one that is not pressurized in each case Chamber open against the return.

Durch die aufgezeigte Gestaltung ist ein in Achsrichtung der Nockenwelle 2 sehr kurz bauender Nockenwellenversteller 1 gegeben, bei dem der Innenkörper 110 über die Spannschraube 9 axial gegen die Nockenwelle 2 verspannt und zugleich zentriert ist, wobei die Spannschraube 9 ihrerseits zugleich die Zentrierung für den Innenkörper 110 bildet.Due to the design shown in the axial direction Given camshaft 2 very short camshaft adjuster 1, in which the inner body 110 axially via the clamping screw 9 clamped against the camshaft 2 and at the same time centered, the clamping screw 9 in turn also the centering forms for the inner body 110.

Claims (3)

  1. A camshaft adjuster for internal combustion engines which is situated in the drive of camshaft (2) from the crankshaft and is to be connected to the camshaft (2) centred and coaxially in relation thereto, with an inner body (110) which is unable to move rotationally in relation to the camshaft (2) and through which runs a tensioning screw (9) by means of which it can be tensioned axially against the camshaft (2), with an outer body (111) which is able to move rotationally in relation to the inner body (110) and via which the drive connection runs to the crankshaft, with a receiving chamber between the inner body (110) and the outer body (111) for actuating means subject to hydraulic forces to rotate the outer body (111) in relation to the inner body (110) and with a control device assigned to these actuating means with a multi-way valve which is integrated into the tensioning screw (9) and which forms an axial receiver for a centrally located and axially movable control slide (8) as a housing,
    characterised in that
    the end of the tensioning screw (9) nearest the camshaft (2) engages in an axial centring shoulder (119) in the camshaft (2), is centred in relation thereto circumferentially and supports the inner body (110) as the element centring the camshaft adjuster (1) in relation to the camshaft (2), that the inner body (110) and the outer body (111) are provided with piston fins (13, 14) which are angled radially in opposing directions and divide the receiving chamber between the inner body (110) and the outer body (111) into operating chambers (16, 17) subject to hydraulic forces and that the inner body (110) and the outer body (111) have flat ends and are covered by ring covers (134, 135) which laterally bound the working chambers (16, 17).
  2. A camshaft adjuster in accordance with claim 1,
    characterised in that
    the ring covers (134, 135) are radially adjacent to the centring shoulder (119) of the camshaft (2) internally.
  3. A camshaft adjuster in accordance with claim 1 or 2,
    characterised in that
    the control slide (8) is connected to the armature (7) of an actuator (5) which is fixed rigidly to a housing and comprises an operating magnet.
EP99916918A 1998-04-18 1999-04-14 Camshaft adjuster for internal combustion engines Expired - Lifetime EP1073830B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19817319 1998-04-18
DE19817319A DE19817319C2 (en) 1998-04-18 1998-04-18 Camshaft adjuster for internal combustion engines
PCT/EP1999/002495 WO1999054599A1 (en) 1998-04-18 1999-04-14 Camshaft adjuster for internal combustion engines

Publications (2)

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EP1073830A1 EP1073830A1 (en) 2001-02-07
EP1073830B1 true EP1073830B1 (en) 2002-09-25

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EP (1) EP1073830B1 (en)
DE (2) DE19817319C2 (en)
WO (1) WO1999054599A1 (en)

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Publication number Publication date
EP1073830A1 (en) 2001-02-07
DE19817319C2 (en) 2001-12-06
DE19817319A1 (en) 1999-10-28
WO1999054599A1 (en) 1999-10-28
DE59902848D1 (en) 2002-10-31
US6363896B1 (en) 2002-04-02

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