EP1507961A1 - Camshaft adjuster - Google Patents

Camshaft adjuster

Info

Publication number
EP1507961A1
EP1507961A1 EP03714873A EP03714873A EP1507961A1 EP 1507961 A1 EP1507961 A1 EP 1507961A1 EP 03714873 A EP03714873 A EP 03714873A EP 03714873 A EP03714873 A EP 03714873A EP 1507961 A1 EP1507961 A1 EP 1507961A1
Authority
EP
European Patent Office
Prior art keywords
pressure
locking bolt
impeller
locking
internal combustion
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.)
Withdrawn
Application number
EP03714873A
Other languages
German (de)
French (fr)
Inventor
Jens Plank
Jörg RÖSENER
Holger Rudzinski
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.)
Mercedes Benz Group AG
Original Assignee
DaimlerChrysler AG
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 DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP1507961A1 publication Critical patent/EP1507961A1/en
Withdrawn legal-status Critical Current

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
    • 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
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis

Definitions

  • the invention relates to a camshaft adjuster according to the preamble of claim 1.
  • Camshaft adjusters are used in valve-controlled internal combustion engines to change the rotational position of the camshaft relative to the crankshaft. As a result, the opening times of the gas exchange valves are adjusted relative to the top dead center of a piston in the direction of early or late to optimize the change in charge of the combustion chambers or cylinders in dependence on the respective operating point of the internal combustion engine.
  • a camshaft adjuster which has an impeller. This is rotatably connected to the camshaft and limited rotatably mounted in a drive part, which is usually driven by a toothed belt of the crankshaft of the internal combustion engine.
  • the impeller engages with its wings in intermediate spaces of the drive part, which are formed by radially inwardly facing projections.
  • the projections limit the maximum angle of rotation by which the impeller can be rotated relative to the drive part.
  • hydraulic pressure chambers are formed, which are controlled by a control valve, so that the relative position of the impeller to the drive part of the Pressure conditions of the pressure chambers results, which lie in the circumferential direction on both sides of a wing.
  • the impeller In the operating pauses of the internal combustion engine, the impeller is adjusted by springs in one of the two end positions and locked by a locking bolt which is mounted axially displaceable either in the impeller or in the drive member and engages in a locking bore of the other part.
  • the camshaft In the locked end position of the impeller, the camshaft must assume a rotational angle position to the crankshaft, in which the internal combustion engine can be started low. After starting, the rotational angle position is controlled or regulated in accordance with an operating map of the internal combustion engine. Since the locked end position limits the adjustment of the camshaft to early or late, it is not possible to operate the gas exchange valves during operation sooner or later.
  • a locking of the impeller during the starting phase is therefore necessary so that the impeller does not move unintentionally by vibrations or the like during the starting phase, in which the impeller is not yet stabilized by an actuating pressure.
  • Camshaft adjusters are also adapted to change the angular position of two camshafts against each other, of which the one intake valves and the other exhaust valves are assigned.
  • the object of the invention is to improve the operating behavior of the internal combustion engine by means of a larger Adjust the angle at the camshaft.
  • the object is achieved by the features of claim 1.
  • the locked position between two end positions of the impeller is arranged and not assigned to the end positions of the impeller. This makes it possible, during the operating phase, to adjust the camshaft over the position blocked during the starting phase, both in the direction of early and late, so that the operating behavior of the internal combustion engine is not limited, as in the prior art, by an end position assumed during the starting phase is.
  • the locking bolt is acted upon during a starting phase of the internal combustion engine against the compression spring only by a control valve generated by the adjusting pressure for the impeller until complete unlocking, while the unlocked position during the operating life of the internal combustion engine by a System pressure is maintained.
  • the locking bolt has a central bore, which is connected on the one hand via a radial bore with an annular groove and on the other hand opens into an effective piston surface, such as an end face of the locking bolt, which faces a locking hole.
  • the pressure chamber formed between the end face of the locking bolt and the locking bore formed as a blind bore is connected via the annular groove in the locked position of the locking bolt with an actuating pressure port and in the unlocked position of the locking bolt with a System horran- circuit, the other port is locked.
  • the locking bolt is initially adjusted by the actuating pressure, wherein the actuating pressure port closes with increasing displacement, while the system pressure port opens accordingly.
  • the actuating pressure port In the unlocked position, the actuating pressure port is completely closed, so that no pressure oil can pass through the annular groove from the system pressure port into the actuating pressure port.
  • Fig. 3 is a schematic longitudinal section through a locking device in a locked position
  • Fig. 4 is a schematic longitudinal section through a locking device in an unlocked position.
  • a camshaft adjuster 10 has a drive part 11, which is connected in a conventional manner in terms of drive with a crankshaft or a second camshaft, which are not shown here.
  • an impeller 12 is mounted rotatably limited.
  • the adjustment direction 21 it can adjust the camshaft connected to it in a rotationally fixed manner so that the gas exchange valves are actuated later, while in the opposite adjustment direction 22 the gas exchange valves are actuated earlier.
  • the phaser 10 may also be used to adjust the timing of intake valves relative to the timing of exhaust valves.
  • the relative adjustment of the impeller 12 relative to the drive member 11 is carried out hydraulically by wings 13, 14 engage in intermediate spaces of the drive member 11, which are formed by projections 15. Between the wings 13, 14 on the one hand and the projections 15 on the other hand, on both sides of the wings 13, 14 chambers 18, 19 are formed, which via a not-shown control valve a Actuating pressure is supplied. According to the pressure conditions in the chambers 18, 19, which extend radially between a base circle 16 and a circumferential circle 17, the impeller 12 is displaced relative to the drive member 11 in the adjustment direction 21 and 22 respectively.
  • the camshaft adjuster 10 has a locking mechanism consisting of a locking bore 24 in the form of a blind bore in a cover 20 of the drive member 11 and a locking pin 23 which is acted upon by a compression spring 30 at one end and with its other end in a locked position in the Locking hole 24 engages.
  • the locked position shown in Figs. 2 and 3 occupies the impeller 12 during the pauses of the internal combustion engine. This position ensures optimal valve timing for the start of the engine.
  • a pressure chamber 33 which is formed between an end face of the locking bolt 23 and the locking hole 24, connected via a central bore 28, a radial bore 27 and an annular groove 26 with an actuating pressure port 25.
  • This opens, for example, in the pressure chamber 19. If during the starting phase of the internal combustion engine in the pressure chamber 19, the actuating pressure over a certain amount, which is determined by the end face of the locking bolt 23 and the spring force of the compression spring 30, the locking pin 23 moves in the unlocking direction and decreases 4, in which the actuating pressure port 25 is closed by the locking pin 23 and the annular groove 26 is connected to a system pressure port 29, so that the locking pin 23 remains in the unlocked position, as long as on the internal combustion engine of the system is made available. This ensures that the locking pin 23 when passing over the locking hole 24 during operation of the internal combustion engine does not accidentally penetrate into the locking hole 24.
  • a spring chamber 31 in which the compression spring 30 is housed.
  • the spring chamber 31 is connected via a relief bore 32 with a non-pressurized space.
  • the locking pin 23 is provided in the impeller 12 and the locking bore 24 in the drive member 11. These positions can also be reversed. Furthermore, Figs. 1 and 2 show that the wings 13 in the circumferential direction have a smaller extent than the wings 14, which are provided for receiving the locking pin 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a camshaft adjuster for an internal combustion engine comprising a blade wheel, which is rotationally connected to a camshaft and which is mounted in a driving part whereby being able to rotate in a limited manner. Starting from an inner base circle and extending to an outer peripheral circle, the blade wheel, with its blades, engages inside intermediate spaces formed by radial projections of the driving part. A pressure chamber is formed in the peripheral direction on both sides of a blade and can be supplied with pressure oil via a control valve so that the blade wheel is displaced relative to the driving part about a rotation angle according to the pressure ratios existing inside the pressure chambers. In addition, a locking bolt, which can be hydraulically unlocked and which is subjected to the action of a pressure spring in a direction of locking, couples the blade wheel to the driving part in a locked position. The locked position is situated between two final positions of the blade wheel.

Description

Nockenwellenversteller Phaser
Die Erfindung betrifft einen Nockenwellenversteller nach dem Oberbegriff des Anspruchs 1.The invention relates to a camshaft adjuster according to the preamble of claim 1.
Nockenwellenversteller werden bei ventilgesteuerten Brennkraftmaschinen eingesetzt, um die Drehwinkellage der Nockenwelle gegenüber der Kurbelwelle zu verändern. Dadurch werden die Öffnungszeiten der Gaswechselventile relativ zum oberen Totpunkt eines Kolbens in Richtung früh oder spät verstellt, um den LadungsWechsel der Brennräume bzw. Zylinder in Abhängigkeit vom jeweiligen Betriebspunkt der Brennkraftmaschine zu optimieren.Camshaft adjusters are used in valve-controlled internal combustion engines to change the rotational position of the camshaft relative to the crankshaft. As a result, the opening times of the gas exchange valves are adjusted relative to the top dead center of a piston in the direction of early or late to optimize the change in charge of the combustion chambers or cylinders in dependence on the respective operating point of the internal combustion engine.
Aus der DE 196 23 818 AI ist ein Nockenwellenversteller bekannt, der ein Flügelrad besitzt. Dieses ist drehfest mit der Nockenwelle verbunden und begrenzt drehbar in einem Antriebsteil gelagert, das in der Regel über einen Zahnriemen von der Kurbelwelle der Brennkraftmaschine angetrieben wird. Das Flügelrad greift mit seinen Flügeln in Zwischenräume des Antriebsteils, die von radial nach innen weisenden Vorsprüngen gebildet werden. Die Vorsprünge begrenzen den maximalen Drehwinkel, um den das Flügelrad relativ zum Antriebsteil verdreht werden kann. Zwischen den Flügeln und den Vorsprüngen werden hydraulische Druckkammern gebildet, die über ein Steuerventil angesteuert werden, so dass sich die relative Lage des Flügelrads zum Antriebsteil aus den Druckverhältnissen der Druckkammern ergibt, die in Umfangsrichtung zu beiden Seiten eines Flügels liegen. In den Betriebspausen der Brennkraftmaschine wird das Flügelrad durch Federn in eine der beiden Endlagen verstellt und durch einen Verriegelungsbolzen verriegelt, der entweder im Flügelrad oder im Antriebsteil axial verschiebbar gelagert ist und in eine Verriegelungsbohrung des jeweils anderen Teils eingreift. In der verriegelten Endlage des Flügelrads muss die Nockenwelle eine Drehwinkelposition zur Kurbelwelle einnehmen, in der die Brennkraftmaschine günstig gestartet werden kann. Nach dem Start wird die Drehwinkellage entsprechend einem Betriebskennfeld der Brennkraftmaschine gesteuert oder geregelt . Da die verriegelte Endlage die Verstellung der Nockenwelle nach früh oder spät begrenzt, ist es nicht möglich, die Gaswechselventile während des Betriebs darüber hinaus früher bzw. später zu betätigen.From DE 196 23 818 AI a camshaft adjuster is known which has an impeller. This is rotatably connected to the camshaft and limited rotatably mounted in a drive part, which is usually driven by a toothed belt of the crankshaft of the internal combustion engine. The impeller engages with its wings in intermediate spaces of the drive part, which are formed by radially inwardly facing projections. The projections limit the maximum angle of rotation by which the impeller can be rotated relative to the drive part. Between the wings and the projections hydraulic pressure chambers are formed, which are controlled by a control valve, so that the relative position of the impeller to the drive part of the Pressure conditions of the pressure chambers results, which lie in the circumferential direction on both sides of a wing. In the operating pauses of the internal combustion engine, the impeller is adjusted by springs in one of the two end positions and locked by a locking bolt which is mounted axially displaceable either in the impeller or in the drive member and engages in a locking bore of the other part. In the locked end position of the impeller, the camshaft must assume a rotational angle position to the crankshaft, in which the internal combustion engine can be started low. After starting, the rotational angle position is controlled or regulated in accordance with an operating map of the internal combustion engine. Since the locked end position limits the adjustment of the camshaft to early or late, it is not possible to operate the gas exchange valves during operation sooner or later.
Eine Verriegelung des Flügelrads während der Startphase ist deshalb notwendig, damit sich das Flügelrad nicht ungewollt durch Schwingungen oder dergleichen während der Startphase verstellt, in der das Flügelrad noch nicht durch einen Betätigungsdruck stabilisiert ist. Sobald ein Betätigungsdruck in einer der Kammern aufgebaut wird, und sich dadurch die Lage des Flügelrads stabilisiert hat, wird der Verriegelungsbolzen durch den Betätigungsdruck aus der Verriegelungsbohrung zurückgeschoben und bleibt in der entriegelten Position, solange eine der Druckkammern beaufschlagt ist.A locking of the impeller during the starting phase is therefore necessary so that the impeller does not move unintentionally by vibrations or the like during the starting phase, in which the impeller is not yet stabilized by an actuating pressure. Once an actuation pressure is built up in one of the chambers, and thereby the position of the impeller has stabilized, the locking bolt is pushed back by the actuating pressure from the locking bore and remains in the unlocked position, as long as one of the pressure chambers is applied.
Nockenwellenversteller sind auch geeignet, um die Drehwinkellage zweier Nockenwellen gegeneinander zu verändern, von denen die eine Einlassventilen und die andere Auslassventilen zugeordnet sind.Camshaft adjusters are also adapted to change the angular position of two camshafts against each other, of which the one intake valves and the other exhaust valves are assigned.
Die Aufgabe der Erfindung besteht darin, das Betriebsverhalten der Brennkraftmaschine durch einen größeren Ver- Stellwinkel an der Nockenwelle zu optimieren. Die Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen.The object of the invention is to improve the operating behavior of the internal combustion engine by means of a larger Adjust the angle at the camshaft. The object is achieved by the features of claim 1. Advantageous embodiments and modifications of the invention will become apparent from the dependent claims.
Nach der Erfindung ist die verriegelte Stellung zwischen zwei Endlagen des Flügelrads angeordnet und nicht den Endlagen des Flügelrads zugeordnet. Dadurch ist es möglich, während der Betriebsphase die Nockenwelle über die während der Startphase blockierte Stellung sowohl in Richtung früh als auch in Richtung spät zu verstellen, so dass das Betriebsverhalten der Brennkraftmaschine nicht wie beim Stand der Technik durch eine, während der Startphase eingenommene Endlage begrenzt ist.According to the invention, the locked position between two end positions of the impeller is arranged and not assigned to the end positions of the impeller. This makes it possible, during the operating phase, to adjust the camshaft over the position blocked during the starting phase, both in the direction of early and late, so that the operating behavior of the internal combustion engine is not limited, as in the prior art, by an end position assumed during the starting phase is.
Da die Zwischenlage in den Betriebspausen der Brennkraftmaschine sicher angefahren und verriegelt werden muss, ist sicherzustellen, dass während der Betriebsphase der Brennkraftmaschine die Zwischenstellung überfahren werden kann, ohne dass der Verriegelungsbolzen ungewollt in die Verriegelungsbohrung einfährt. Gemäß einer Ausgestaltung der Erfindung wird daher vorgeschlagen, dass der Verriegelungs- bolzen während einer Startphase der Brennkraftmaschine entgegen der Druckfeder nur von einem vom Steuerventil erzeugten Verstelldruck für das Flügelrad bis zum vollständigen Entriegeln beaufschlagt wird, während die entriegelte Stellung während der Betriebsdauer der Brennkraftmaschine durch einen Systemdruck gehalten wird. Dadurch wird gewährleistet, dass der Entriegelungsbolzen nicht entriegelt wird, bevor der Betätigungsdruck das Flügelrad in seiner Stellung stabilisiert und dass er unabhängig vom Betätigungsdruck anschließend durch den Systemdruck in der verriegelten Stellung gehalten wird, bis die Brennkraftmaschine stoppt und der Systemdruck wieder abfällt. Gemäß einer weiteren Ausgestaltung der Erfindung wird hierzu vorgeschlagen, dass der Verriegelungsbolzen eine zentrale Bohrung aufweist, die einerseits über eine radiale Bohrung mit einer Ringnut verbunden ist und andererseits in einer wirksamen Kolbenfläche, z.B. einer Stirnfläche des Verriegelungsbolzens mündet, die einer Verriegelungsbohrung zugewandt ist. Dem zwischen der Stirnfläche des Verriegelungsbolzens und der als Sackbohrung ausgebildeten Verriegelungsbohrung gebildete Druckraum ist über die Ringnut in der verriegelten Stellung des Verriegelungsbolzens mit einem Betätigungsdruckanschluss und in der entriegelten Stellung des Verriegelungsbolzens mit einem Systemdruckan- schluss verbunden, wobei der jeweils andere Anschluss gesperrt ist. Somit wird der Verriegelungsbolzen zunächst von dem Betätigungsdruck verstellt, wobei sich der Betätigungsdruckanschluss mit zunehmendem Verstellweg schließt, während sich der Systemdruckanschluss entsprechend öffnet . In der entriegelten Stellung ist der Betätigungsdruckanschluss vollständig geschlossen, so dass kein Drucköl über die Ringnut vom Systemdruckanschluss in den Betätigungsdruckanschluss gelangen kann.Since the liner must be safely started and locked in the operating pauses of the internal combustion engine, it must be ensured that during the operating phase of the internal combustion engine, the intermediate position can be run over without the locking bolt unintentionally enters into the locking hole. According to one embodiment of the invention, it is therefore proposed that the locking bolt is acted upon during a starting phase of the internal combustion engine against the compression spring only by a control valve generated by the adjusting pressure for the impeller until complete unlocking, while the unlocked position during the operating life of the internal combustion engine by a System pressure is maintained. This will ensure that the unlatching bolt will not be unlatched before the actuating pressure stabilizes the impeller in position and is held in the latched position by the system pressure regardless of the actuation pressure until the engine stops and the system pressure drops again. According to a further embodiment of the invention, it is proposed for this purpose that the locking bolt has a central bore, which is connected on the one hand via a radial bore with an annular groove and on the other hand opens into an effective piston surface, such as an end face of the locking bolt, which faces a locking hole. The pressure chamber formed between the end face of the locking bolt and the locking bore formed as a blind bore is connected via the annular groove in the locked position of the locking bolt with an actuating pressure port and in the unlocked position of the locking bolt with a Systemdruckan- circuit, the other port is locked. Thus, the locking bolt is initially adjusted by the actuating pressure, wherein the actuating pressure port closes with increasing displacement, while the system pressure port opens accordingly. In the unlocked position, the actuating pressure port is completely closed, so that no pressure oil can pass through the annular groove from the system pressure port into the actuating pressure port.
Damit sich durch Lecköl in einem Federraum der Druckfeder kein hydraulischer Druck aufbauen kann, ist es zweckmäßig, den Federraum über eine Entlastungsbohrung mit einem drucklosen Raum zu verbinden.So that no hydraulic pressure can build up through leakage oil in a spring chamber of the compression spring, it is expedient to connect the spring chamber via a relief bore with a non-pressurized space.
Weitere Vorteile ergeben sich aus der folgenden Zeichnungs- beschreibung. In der Zeichnung ist ein Ausführungsbeispiel der Erfindung dargestellt. Die Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination. Der Fachmann wird die Merkmale zweckmäßigerweise auch einzeln betrachten und zu sinnvollen weiteren Kombinationen zusammenfassen. Es zeigt :Further advantages result from the following description of the drawing. In the drawing, an embodiment of the invention is shown. The description and claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations. It shows :
Fig. 1 einen schematischen Querschnitt durch einen Nockenwellenversteller in einer entriegelten Stellung,1 shows a schematic cross section through a camshaft adjuster in an unlocked position,
Fig. 2 einen schematischen Querschnitt durch einen Nockenwellenversteller in einer verriegelten Stellung,2 shows a schematic cross section through a camshaft adjuster in a locked position,
Fig. 3 einen schematischen Längsschnitt durch eine Verriegelungseinrichtung in einer verriegelten Stellung undFig. 3 is a schematic longitudinal section through a locking device in a locked position and
Fig. 4 einen schematischen Längsschnitt durch eine Verriegelungseinrichtung in einer entriegelten Stellung.Fig. 4 is a schematic longitudinal section through a locking device in an unlocked position.
Ein Nockenwellenversteller 10 besitzt ein Antriebsteil 11, das in üblicher Weise triebmäßig mit einer Kurbelwelle oder einer zweiten Nockenwelle verbunden ist, die hier aber nicht dargestellt sind. In dem Antriebsteil 11 ist ein Flügelrad 12 begrenzt drehbar gelagert. Es kann in Verstell- richtung 21 die mit ihm drehfest verbundene Nockenwelle so verstellen, dass die Gaswechselventile später betätigt werden, während in der entgegengesetzten Verstellrichtung 22 die Gaswechselventile früher betätigt werden. Der Nockenwellenversteller 10 kann auch dazu genutzt werden, um die Steuerzeiten von Einlassventilen relativ zu den Steuerzeiten von Auslassventilen zu verstellen.A camshaft adjuster 10 has a drive part 11, which is connected in a conventional manner in terms of drive with a crankshaft or a second camshaft, which are not shown here. In the drive part 11, an impeller 12 is mounted rotatably limited. In the adjustment direction 21, it can adjust the camshaft connected to it in a rotationally fixed manner so that the gas exchange valves are actuated later, while in the opposite adjustment direction 22 the gas exchange valves are actuated earlier. The phaser 10 may also be used to adjust the timing of intake valves relative to the timing of exhaust valves.
Die relative Verstellung des Flügelrads 12 gegenüber dem Antriebsteil 11 erfolgt hydraulisch, indem Flügel 13, 14 in Zwischenräume des Antriebsteils 11 eingreifen, die durch Vorsprünge 15 gebildet werden. Zwischen den Flügeln 13, 14 einerseits und den Vorsprüngen 15 andererseits werden zu beiden Seiten der Flügel 13, 14 Kammern 18, 19 gebildet, denen über ein nicht näher dargestelltes Steuerventil ein Betätigungsdruck zugeführt wird. Entsprechend den Druckverhältnissen in den Kammern 18, 19, die sich radial zwischen einem Grundkreis 16 und einem Umfangskreis 17 erstrecken, wird das Flügelrad 12 relativ zum Antriebsteil 11 in die Verstellrichtung 21 bzw. 22 verschoben.The relative adjustment of the impeller 12 relative to the drive member 11 is carried out hydraulically by wings 13, 14 engage in intermediate spaces of the drive member 11, which are formed by projections 15. Between the wings 13, 14 on the one hand and the projections 15 on the other hand, on both sides of the wings 13, 14 chambers 18, 19 are formed, which via a not-shown control valve a Actuating pressure is supplied. According to the pressure conditions in the chambers 18, 19, which extend radially between a base circle 16 and a circumferential circle 17, the impeller 12 is displaced relative to the drive member 11 in the adjustment direction 21 and 22 respectively.
Der Nockenwellenversteller 10 besitzt einen Verriegelungs- mechanismus bestehend aus einer Verriegelungsbohrung 24 in Form einer Sackbohrung in einem Deckel 20 des Antriebsteils 11 und einem Verriegelungsbolzen 23, der an einem Ende durch eine Druckfeder 30 beaufschlagt ist und mit seinem anderen Ende in einer verriegelten Stellung in die Verriegelungsbohrung 24 eingreift. Die in Fig. 2 und 3 dargestellte verriegelte Stellung nimmt das Flügelrad 12 während der Betriebspausen der Brennkraftmaschine ein. Diese Stellung gewährleistet für den Start der Brennkraftmaschine optimale Ventilsteuerzeiten.The camshaft adjuster 10 has a locking mechanism consisting of a locking bore 24 in the form of a blind bore in a cover 20 of the drive member 11 and a locking pin 23 which is acted upon by a compression spring 30 at one end and with its other end in a locked position in the Locking hole 24 engages. The locked position shown in Figs. 2 and 3 occupies the impeller 12 during the pauses of the internal combustion engine. This position ensures optimal valve timing for the start of the engine.
Zum Entriegeln des Verriegelungsbolzens 23 wird eine Druckkammer 33, die zwischen einer Stirnfläche des Verriegelungsbolzens 23 und der Verriegelungsbohrung 24 gebildet ist, über eine zentrale Bohrung 28, eine radiale Bohrung 27 und eine Ringnut 26 mit einem Betätigungsdruckanschluss 25 verbunden. Dieser mündet z.B. in der Druckkammer 19. Steigt während der Startphase der Brennkraftmaschine in der Druckkammer 19 der Betätigungsdruck über einen bestimmten Betrag, der durch die Stirnfläche des Verriegelungsbolzens 23 und der Federkraft der Druckfeder 30 bestimmt wird, bewegt sich der Verriegelungsbolzen 23 in Entriegelungsrichtung und nimmt schließlich die in Fig. 4 dargestellte Entriegelungsstellung ein, in der der Betätigungsdruckanschluss 25 durch den Verriegelungsbolzen 23 geschlossen ist und die Ringnut 26 mit einem Systemdruckanschluss 29 verbunden ist, so dass der Verriegelungsbolzen 23 in der entriegelten Stellung bleibt, solange an der Brennkraftmaschine der Sys- temdruck zur Verfügung gestellt wird. Damit ist sichergestellt, dass der Verriegelungsbolzen 23 beim Überfahren der Verriegelungsbohrung 24 während des Betriebs der Brennkraftmaschine nicht ungewollt in die Verriegelungsbohrung 24 eindringt.To unlock the locking bolt 23, a pressure chamber 33, which is formed between an end face of the locking bolt 23 and the locking hole 24, connected via a central bore 28, a radial bore 27 and an annular groove 26 with an actuating pressure port 25. This opens, for example, in the pressure chamber 19. If during the starting phase of the internal combustion engine in the pressure chamber 19, the actuating pressure over a certain amount, which is determined by the end face of the locking bolt 23 and the spring force of the compression spring 30, the locking pin 23 moves in the unlocking direction and decreases 4, in which the actuating pressure port 25 is closed by the locking pin 23 and the annular groove 26 is connected to a system pressure port 29, so that the locking pin 23 remains in the unlocked position, as long as on the internal combustion engine of the system is made available. This ensures that the locking pin 23 when passing over the locking hole 24 during operation of the internal combustion engine does not accidentally penetrate into the locking hole 24.
Über die Bewegungsspalte zwischen dem Verriegelungsbolzen 23 und dem Flügel 14 des Flügelrads 12 kann Lecköl in einen Federraum 31 eindringen, in der die Druckfeder 30 untergebracht ist. Um zu vermeiden, dass sich in dem Federraum 31 ein hydraulischer Druck aufbaut, ist der Federraum 31 über eine Entlastungsbohrung 32 mit einem drucklosen Raum verbunden.About the movement gaps between the locking pin 23 and the wing 14 of the impeller 12 can leak oil penetrate into a spring chamber 31, in which the compression spring 30 is housed. In order to avoid that builds up in the spring chamber 31, a hydraulic pressure, the spring chamber 31 is connected via a relief bore 32 with a non-pressurized space.
Bei der dargestellten Ausführung ist der Verriegelungsbolzen 23 in dem Flügelrad 12 und die Verriegelungsbohrung 24 im Antriebsteil 11 vorgesehen. Diese Positionen können auch vertauscht werden. Ferner lassen die Fig. 1 und 2 erkennen, dass die Flügel 13 in Umfangsrichtung eine geringere Erstreckung aufweisen als die Flügel 14, die für die Aufnahme der Verriegelungsbolzen 23 vorgesehen sind. In the illustrated embodiment, the locking pin 23 is provided in the impeller 12 and the locking bore 24 in the drive member 11. These positions can also be reversed. Furthermore, Figs. 1 and 2 show that the wings 13 in the circumferential direction have a smaller extent than the wings 14, which are provided for receiving the locking pin 23.

Claims

PatentansprücheClaims
1. Nockenwellenversteller für eine Brennkraftmaschine mit einem mit einer Nockenwelle drehfest verbundenen Flügelrad, das begrenzt drehbar in einem Antriebsteil gelagert ist und mit seinen Flügeln von einem inneren Grundkreis ausgehend bis zu einem äußeren Umfangskreis in Zwischenräume eingreift, die von radialen Vorsprüngen des Antriebsteils gebildet werden, wobei in Umfangsrichtung zu beiden Seiten eines Flügels jeweils eine Druckkammer entsteht, der über ein Steuerventil Drucköl zugeführt werden kann, so dass sich das Flügelrad entsprechend der sich in den Druckkammern einstellenden Druckverhältnisse relativ zum Antriebsteil um einen Drehwinkel verstellt, und wobei ein hydraulisch entriegelbarer, in eine Verriegelungsrichtung durch eine Druckfeder belasteter Verriegelungsbolzen das Flügelrad in einer verriegelten Stellung mit dem Antriebsteil koppelt, dadurch gekennzeichnet, dass die verriegelte Stellung zwischen zwei Endlagen des Flügelrads (12) angeordnet ist.1.Camshaft adjuster for an internal combustion engine with an impeller rotatably connected to a camshaft, which is rotatably supported in a drive part to a limited extent and engages with its vanes starting from an inner base circle up to an outer circumferential circle in spaces which are formed by radial projections of the drive part. whereby a pressure chamber is created in the circumferential direction on both sides of a vane, which pressure oil can be supplied via a control valve, so that the vane wheel is adjusted by an angle of rotation relative to the drive part in accordance with the pressure conditions established in the pressure chambers, and wherein a hydraulically unlockable, in a locking direction by a compression spring loaded locking bolt couples the impeller in a locked position to the drive part, characterized in that the locked position is arranged between two end positions of the impeller (12).
2. Nockenwellenversteller nach Anspruch 1, dadurch gekennzeichnet, dass der Verriegelungsbolzen (23) während einer Startphase der Brennkraftmaschine entgegen der Druckfeder2. Camshaft adjuster according to claim 1, characterized in that the locking bolt (23) during a starting phase of the internal combustion engine against the compression spring
(30) nur von einem vom Steuerventil erzeugten Verstelldruck für das Flügelrad (13) bis zum vollständigen Entriegeln beaufschlagt wird, während die entriegelte Stellung während der Betriebsdauer der Brennkraftmaschine durch einen Systemdruck gehalten wird.(30) is only acted upon by an adjustment pressure generated by the control valve for the impeller (13) until fully unlocked, while the unlocked position during the operating time of the internal combustion engine is maintained by a system pressure.
3. Nockenwellenversteller nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Verriegelungsbolzen (23) eine zentrale Bohrung (28) aufweist, die einerseits über eine radiale Bohrung (27) mit einer Ringnut (26) verbunden ist und andererseits in einer Stirnfläche des Verriegelungsbolzens (23) mündet, die einer Verriegelungs- bohrung (24) zugewandt ist, wobei die Ringnut (26) in der verriegelten Stellung des Verriegelungsbolzens (23) mit einem Betätigungsdruckanschluss (25) und in der entriegelten Stellung des Verriegelungsbolzens (23) mit einem Systemdruckanschluss (29) verbunden ist, wobei der jeweils andere Anschluss (25 bzw. 29) gesperrt ist.3. Camshaft adjuster according to one of the preceding claims, characterized in that the locking bolt (23) has a central bore (28) which is connected on the one hand via a radial bore (27) with an annular groove (26) and on the other hand in an end face of the locking bolt (23) opens, which faces a locking bore (24), the annular groove (26) in the locked position of the locking bolt (23) with an actuating pressure connection (25) and in the unlocked position of the locking bolt (23) with a system pressure connection (29) is connected, the other connection (25 or 29) being blocked.
4. Nockenwellenversteller nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Druckfeder (30) in einem Federraum (31) angeordnet ist, der über eine Entlastungsbohrung (32) mit einem drucklosen Raum verbunden ist . 4. Camshaft adjuster according to one of the preceding claims, characterized in that the compression spring (30) is arranged in a spring chamber (31) which is connected to a pressure-free space via a relief bore (32).
EP03714873A 2002-05-25 2003-03-22 Camshaft adjuster Withdrawn EP1507961A1 (en)

Applications Claiming Priority (3)

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DE10223409 2002-05-25
DE10223409A DE10223409A1 (en) 2002-05-25 2002-05-25 Phaser
PCT/EP2003/003002 WO2003100222A1 (en) 2002-05-25 2003-03-22 Camshaft adjuster

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DE102004038171A1 (en) * 2004-08-06 2006-03-16 Daimlerchrysler Ag Device for adjusting a camshaft and method for operating a device for adjusting a camshaft
EP1681442A1 (en) * 2005-01-18 2006-07-19 Delphi Technologies, Inc. Phaser for controlling the timing between a camshaft and a timing gear
GB2437305B (en) * 2006-04-19 2011-01-12 Mechadyne Plc Hydraulic camshaft phaser with mechanical lock
WO2012094324A1 (en) 2011-01-04 2012-07-12 Hilite Germany Gmbh Valve timing control apparatus and method
US8973542B2 (en) 2012-09-21 2015-03-10 Hilite Germany Gmbh Centering slot for internal combustion engine
US9366161B2 (en) 2013-02-14 2016-06-14 Hilite Germany Gmbh Hydraulic valve for an internal combustion engine
DE102014205568B4 (en) 2014-03-26 2017-05-04 Schaeffler Technologies AG & Co. KG Camshaft adjustment device
US9784143B2 (en) 2014-07-10 2017-10-10 Hilite Germany Gmbh Mid lock directional supply and cam torsional recirculation

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GB2302391B (en) * 1995-06-14 1999-08-18 Nippon Denso Co Control apparatus for varying the rotational or angular phase between two rotational shafts
JP3787899B2 (en) * 1996-07-12 2006-06-21 アイシン精機株式会社 Valve timing control device
JPH11241608A (en) * 1997-12-24 1999-09-07 Toyota Motor Corp Valve timing control mechanism of internal combustion engine
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DE10223409A1 (en) 2003-12-04
US6968818B2 (en) 2005-11-29

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