EP1749146B1 - Camshaft adjuster - Google Patents

Camshaft adjuster Download PDF

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Publication number
EP1749146B1
EP1749146B1 EP05737740A EP05737740A EP1749146B1 EP 1749146 B1 EP1749146 B1 EP 1749146B1 EP 05737740 A EP05737740 A EP 05737740A EP 05737740 A EP05737740 A EP 05737740A EP 1749146 B1 EP1749146 B1 EP 1749146B1
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EP
European Patent Office
Prior art keywords
valve
pressure
valve piston
hydraulic fluid
piston
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Active
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EP05737740A
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German (de)
French (fr)
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EP1749146A1 (en
Inventor
Mike Kohrs
Udo Friedsmann
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP1749146A1 publication Critical patent/EP1749146A1/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
    • 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

Definitions

  • the invention relates to a camshaft adjuster for the relative angular displacement of a camshaft with respect to a driving crankshaft, with a hydraulically actuated adjusting device with chambers in and out of which for angular adjustment on chamber-specific pressure medium channels alternately a hydraulic fluid is zumarinbar and discharged, and with a control valve via which the Hydraulic fluid supplied via a pump can be fed to the pressure medium ducts or discharged from the pressure medium ducts into a tank, whereby working ports A and B leading to the pressure medium ducts, a pressure port P coupleable to the pump and a drain port T coupleable to the tank are provided on the valve body of the control valve , Which working ports A and B depending on the desired angle adjustment via a controlled via a camshaft adjuster externally arranged decoupled tension or pressure magnet movable valve piston huiwei se with the pressure port P or the drain port T are coupled.
  • camshaft via which the valve movement of the intake and exhaust valves of the internal combustion engine is controlled, is motion-coupled to the crankshaft of the engine via a timing chain or timing belt, that is, the camshaft is moved via the crankshaft driven.
  • camshaft adjusters are integrated via which the relative angle that the camshaft to the crankshaft occupies, can be adjusted. That is, both shafts may be slightly twisted relative to one another, with the result that the actuation timing of the valves actuated via the camshaft changes.
  • camshaft adjusters are designed, for example, as vane-type adjusters and comprise a rotor which is connected in a rotationally fixed manner to the camshaft and a stator which is coupled to the crankshaft via the timing chain or the timing belt.
  • rotor On the rotor radially outwardly projecting wings are provided which engage between radially inwardly projecting stops on the stator, which on the one hand limit the twisting movement and on the other hand form chamber walls.
  • the chambers are bounded by the respective side of a rotor-side wing and by the sides of the stator-side stops.
  • a hydraulic fluid is pressed or withdrawn for rotation of the rotor relative to the stator and thus for angular adjustment, including using a control valve, usually a 4/3-way valve , At this working ports A and B are provided, each leading to a chamber A and a chamber B of each chamber pair.
  • the control valve itself is designed as a central valve in the camshaft adjuster configuration in question, it is centrally, inserted centrally in the camshaft adjuster or in its rotor and connected to the camshaft, that is, the control valve rotates with the adjuster or the rotor.
  • a valve piston is integrated, which is axially movable, wherein its displacement is controlled by a camshaft adjuster externally positioned, arranged for example on a motor or other third object train or pressure magnet.
  • the magnet is at this Embodiment thus not integrated in the stage.
  • one or the other working port A or B is now coupled to the pressure port P, so that hydraulic fluid is conducted into the associated chamber A or B, while the respective other chamber is connected to the valve-side drain port, so that the In the unloaded chamber liquid can be withdrawn through the drain port to the tank down.
  • the rotor can be hydraulically rotated with respect to the stator. To hold a set angle of rotation between the stops of the valve piston can close both working ports A and B and thus the associated chambers and almost.
  • the pressure port P is provided with the valve longitudinal axis aligned end face on the valve body.
  • the supplied under pressure hydraulic fluid presses against an end face of the often hollow cylindrical valve piston, before it passes depending on the piston position in the respective working port A or B.
  • the magnetic force counteracts the spring which acts on the valve piston and moves the valve piston into its basic position (P - B - A - T) when the electromagnet is de - energized.
  • the spring is adapted to the system (magnetic force, hydraulic flow and pressure forces, piston travel, piston friction, etc.).
  • the invention is therefore based on the problem of specifying a camshaft adjuster, which allows a secure placement of the valve piston even with high applied fluid pressure.
  • a camshaft adjuster of the type mentioned that the liquid distribution in the control valve, ie in the valve body or the valve piston or between these two, is designed such that the hydraulic fluid at substantially oppositely directed surfaces of the valve piston engages, so act on the valve piston local and each other substantially oppositely directed forces.
  • the flow path for the hydraulic fluid is designed so that the valve piston is loaded by the fluid at two oppositely directed surfaces, so that out set oppositely directed, directed on the valve piston forces that compensate each other at least partially.
  • the total force exerted on the valve piston by the fluid supply is consequently significantly reduced in comparison to the prior art embodiments, which results in that the external control magnet points to the valve piston or its extended control rod pointing towards the magnet , force to be exerted is significantly reduced.
  • any pressure peaks in the supply of hydraulic fluid can in no case adversely affect the valve control.
  • the pressure port P can be perpendicular to the valve axis and open into a connected between the valve piston and the valve body, position-dependent connectable to the working port A annular channel which leads into the hollow cylindrical, closed at both ends valve piston, the cavity position-dependent with the working port B is connectable, wherein the frontal cavity surfaces are acted upon by the hydraulic fluid with pressure.
  • the two working ports can be connected in a position-dependent manner with the outlet connection situated at an angle, preferably perpendicular to the valve longitudinal axis, via a ring channel formed between the valve piston and the valve body.
  • the outlet connection situated at an angle, preferably perpendicular to the valve longitudinal axis, via a ring channel formed between the valve piston and the valve body.
  • both the pressure port P and the drain port T and the working ports A and B perpendicular to the valve axis extending and arranged in the order B- T- A- P or A- T- B- P, wherein In the latter case, a Switzerlandfederr is used to switch the valve in the de-energized state, ie without acting magnet in the basic position P - B - A - T.
  • An alternative embodiment of a control valve provides that the pressure port P is at an angle, preferably perpendicular to the valve axis and opens in a formed between the valve piston and the valve body position-dependent connectable to the working port A or B annulus, wherein the working ports A, B position-dependent via connecting holes can be connected to the cavity of the hollow cylindrical valve piston, which cavity leads to the drain port T, which in this embodiment is axially aligned with the valve longitudinal axis.
  • the pressure port P and the working ports A and B can run perpendicular to the longitudinal axis of the valve and be arranged in the order A-P-B.
  • a further embodiment provides that the pressure port P is located in the valve longitudinal axis and opens via deflecting channels formed in a position-dependent connected to the working port A or B annular space between the valve piston and the valve body, wherein the working ports A, B position-dependent via connecting holes with the cavity the hollow cylindrical valve piston can be connected, which leads cavity to the drain port T.
  • valve embodiment provides that the pressure port P is aligned with the valve longitudinal axis and opens into the hollow cylindrical valve piston, are provided at the radial openings through which the hydraulic fluid passes into the annular space formed between the valve piston and the valve body, from the front side the valve piston is limited.
  • the hydraulic fluid is guided axially into the hollow cylindrical valve piston.
  • the liquid from the piston enters the rear, formed between the piston and the valve body annulus, where it is virtually deflected and presses on the opposite opposite to the cavity end wall piston outer surface. Also in this embodiment, therefore, are virtually opposite each other directed surfaces acted so that oppositely directed local forces act on the valve piston.
  • Fig. 1 shows a control valve 1 consisting of a valve body 2, on which in the illustrated embodiment, an external thread 3 is provided, via which the valve body is screwed camshaft side after insertion into the rotor of an adjustment.
  • a valve piston 4 is guided axially movable, which can be moved against a restoring force generated by a spring 5.
  • a push rod 6 is arranged on the valve piston 4, which cooperates with an external control magnet, not shown in detail, to move the valve piston against the spring or with spring support in the other direction.
  • the control magnet is as described externally arranged for example on the engine, so it does not move, unlike the control valve 1, which rotates with the rotor.
  • the control valve 1 is enclosed encapsulated in the housing of the camshaft adjuster, via which housing the push rod 6 cooperates with the magnet.
  • valve body 2 On the valve body 2 several different connections are provided.
  • a working port A and a working port B are shown, via which a hydraulic fluid can be conveyed into corresponding chambers of the device designed as a vane-cell adjusting device, depending on the position of the valve piston 4.
  • a pressure port P not one of them pump shown in detail, the hydraulic fluid is supplied.
  • a drain port T is shown, is conveyed via the discharged hydraulic fluid in a tank not shown in detail.
  • various control edges 7a (which are assigned to the working port A) and 7b (which are assigned to the working port B) are provided.
  • the working ports A and B are connected via these control edges either to the pressure port P or to the discharge port T via the channel 41, depending on whether fluid is supplied into the chambers, which are assigned to the working port A, and out of the chambers , which are assigned to the working port B, liquid to be discharged and conveyed into the tank via the drain port T, or vice versa.
  • the position is controlled by the magnet not shown in detail.
  • annular channel. 8 provided in the pressure port P opens.
  • valve-piston-side openings 9 of the annular channel opens 8- depending on the piston position in case of need to be connected to the working port A- in the cavity 10 of the valve piston 4.
  • the hydraulic fluid presses in the cavity 10 on two opposite end faces 12, 13, which limit the cavity seen axially. This results in a force F p1 or F p2 directed in each case on the valve piston, which are obviously directed opposite to one another.
  • the two forces - which are ideally equal in the ideal case - thus compensate each other, so that the valve piston 4 in the ideal case virtually quiescent, as far as forces acting on him on the liquid supply.
  • Fig. 2 shows a camshaft adjuster 14 according to the invention, with a rotor 15 and a stator 16.
  • the rotor 15 is rotatably connected to the control valve 1, this mimic is rotatable with respect to the stator 16 which is connected to the timing chain or the timing belt with the crankshaft.
  • a plurality of vanes 17 are provided on the rotor, which bear tightly against the inner wall 18 of the stator and are bounded by the respective two chambers, which are each acted upon via a working port A or B with fluid or withdrawn from there via the respective working fluid connections can. A closer approach to this is not required after the basic design of such camshaft adjuster is well known.
  • Fig. 3 shows a further embodiment according to the invention a camshaft adjuster 19, the basic structure of the camshaft adjuster 14 from Fig. 2 corresponds, but the integrated control valve 20 is constructed differently. It also has a P-pressure port and the two working ports A and B as well as a drain port T. However, here lies the pressure port P, which is guided from the outside via the valve body 21 inwardly, quasi-centered between the working ports A and B, which via the position of the valve piston 22 in a corresponding manner as described with respect to the control valve 1 with the pressure port P or the drain port T, which runs axially here with the valve longitudinal axis, are connectable.
  • the liquid is supplied in such a way that on the valve piston 22 substantially compensating each other, resulting from the pressed liquid forces act.
  • the pressure port P opens into an annular channel 23 which is bounded by the control flanks 24, 25, via which the connection to the working ports A and B are opened or closed.
  • the liquid thus presses on these oppositely directed flanks, so that inevitably set oppositely directed forces that compensate each other.
  • a liquid distribution space is realized, which allows a compensation of forces.
  • FIG. 4 another control valve 26, which can be integrated equally into a phaser as shown in the preceding figures.
  • This control valve also has a valve body 27 and a valve piston 28.
  • the pressure port P is here axially to the valve longitudinal axis, while the working ports A and B, not shown in detail and the drain port T are vertical to the valve longitudinal axis.
  • valve piston is mounted against a return spring 29 here. It is hollow cylindrical, the liquid supplied enters it. On the opposite side, however, a plurality of openings 30 are provided, so that the liquid can enter the surrounding this piston end annular space 31. There, the liquid presses on the piston outer surface 32, which faces the end face 33 in the interior of the piston. Again, two oppositely directed surfaces are thus again subjected to the fluid, so that mutually oppositely directed forces arise, which act on the valve piston 28.
  • FIG. 5 a further control valve 34 according to the invention, whose pressure port P also extends axially, the working ports A and B are on the valve body 35 perpendicular to the longitudinal axis, while the drain port T from the valve piston 36 is vertical to the longitudinal axis.
  • the hydraulic fluid is first deflected via corresponding guide channels 37 and then placed in an annular space 38, the of two surfaces 39, 40 is limited to the valve piston 36.
  • This embodiment substantially corresponds to the valve design Fig. 3 , There are also here equal, but oppositely directed forces on the valve piston 36 a. However, here is the supply of hydraulic fluid axially, while the valve in Fig. 3 done from the side.

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  • 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 the relative angular adjustment of a camshaft with relation to a driving crankshaft, comprising a hydraulically-operated adjuster device with chambers, into which and from which a hydraulic fluid may be alternately introduced or drained through pressure medium channels specific for the chambers to adjust the angle, and a control valve through which the hydraulic fluid supplied by a pump may be introduced into the pressure medium channels or drained from the pressure medium channels into a tank, whereby working connections (A) and (B), leading to the pressure medium channels, a pressure connector (P), coupled to the pump and a drain connector (T), coupled to the tank, are provided on the valve body of the control valve. Said working connections (A) and (B) may be selectively coupled to the pressure connector (P), or the drain connector (T) depending on the desired angle adjustment, by means of a valve piston, the displacement of which is controlled by a remote push- or pull-type solenoid, arranged outside the camshaft, whereby the fluid distribution chamber in the control valve (1, 20, 26, 34) is embodied such that the hydraulic fluid acts on essentially opposed surfaces of the valve piston (4, 22, 28, 36) such that local and essentially opposed forces (Fp1, Fp2) act on said valve piston (4, 22, 28, 36).

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Nockenwellenversteller zur relativen Winkelverstellung einer Nockenwelle bezüglich einer antreibenden Kurbelwelle, mit einer hydraulisch betätigbaren Verstellvorrichtung mit Kammern, in die und aus denen zur Winkelverstellung über kammerspezifische Druckmittelkanäle wechselseitig eine Hydraulikflüssigkeit zu- und abführbar ist, sowie mit einem Steuerventil, über das die über eine Pumpe zugeführte Hydraulikflüssigkeit den Druckmittelkanälen zuführbar bzw. aus den Druckmittelkanälen in einen Tank abführbar ist, wobei am Ventilkörper des Steuerventils zu den Druckmittelkanälen führende Arbeitsanschlüsse A und B, ein mit der Pumpe koppelbarer Druckanschluss P und ein mit dem Tank koppelbarer Ablaufanschluss T vorgesehen ist, welche Arbeitsanschlüsse A und B je nach gewünschter Winkelverstellung über einen über einen zum Nockenwellenversteller extern angeordneten entkoppelten Zug- oder Druckmagneten gesteuert bewegbaren Ventilkolben wahlweise mit dem Druckanschluss P oder dem Ablaufanschluss T koppelbar sind.The invention relates to a camshaft adjuster for the relative angular displacement of a camshaft with respect to a driving crankshaft, with a hydraulically actuated adjusting device with chambers in and out of which for angular adjustment on chamber-specific pressure medium channels alternately a hydraulic fluid is zuführbar and discharged, and with a control valve via which the Hydraulic fluid supplied via a pump can be fed to the pressure medium ducts or discharged from the pressure medium ducts into a tank, whereby working ports A and B leading to the pressure medium ducts, a pressure port P coupleable to the pump and a drain port T coupleable to the tank are provided on the valve body of the control valve , Which working ports A and B depending on the desired angle adjustment via a controlled via a camshaft adjuster externally arranged decoupled tension or pressure magnet movable valve piston wahlwei se with the pressure port P or the drain port T are coupled.

Hintergrund der ErfindungBackground of the invention

Bei bekannten Brennkraftmaschinen ist die Nockenwelle, über die die Ventilbewegung der Einlass- und Auslassventile der Brennkraftmaschine gesteuert wird, mit der Kurbelwelle der Maschine über eine Steuerkette oder einen Steuerriemen bewegungsgekoppelt, das heißt, die Nockenwelle wird über die Kurbelwelle angetrieben. Um abhängig von der Betriebssituation den Betätigungszeitpunkt der Einlass- und/oder Auslassventile verstellen zu können, so dass die Ventile zeitlich gesehen etwas früher oder später bezogen auf den jeweiligen Arbeitstakt öffnen, werden Nockenwellenversteller integriert, über die der relative Winkel, den die Nockenwelle zur Kurbelwelle einnimmt, verstellt werden kann. Das heißt, beide Wellen können relativ zueinander etwas verdreht werden, was zur Folge hat, dass sich der Betätigungszeitpunkt der über die Nockenwelle betätigten Ventile ändert.In known internal combustion engines, the camshaft, via which the valve movement of the intake and exhaust valves of the internal combustion engine is controlled, is motion-coupled to the crankshaft of the engine via a timing chain or timing belt, that is, the camshaft is moved via the crankshaft driven. To be able to adjust the actuation time of the intake and / or exhaust valves depending on the operating situation so that the valves open a little earlier or later relative to the respective power stroke, camshaft adjusters are integrated via which the relative angle that the camshaft to the crankshaft occupies, can be adjusted. That is, both shafts may be slightly twisted relative to one another, with the result that the actuation timing of the valves actuated via the camshaft changes.

Bekannte Nockenwellenversteller sind beispielsweise als Flügelzellenversteller ausgebildet und umfassen einen Rotor, der mit der Nockenwelle drehfest verbunden ist, und einen Stator, der über die Steuerkette oder den Steuerriemen mit der Kurbelwelle gekoppelt ist. Am Rotor sind radial nach außen abstehende Flügel vorgesehen, die zwischen am Stator radial nach innen vorspringende Anschläge, die zum einen die Verdrehbewegung begrenzen und zum anderen Kammerwände bilden, eingreifen. Die Kammern werden durch die jeweilige Seite eines rotorseitigen Flügels sowie durch die Seiten der statorseitigen Anschläge begrenzt. In diese Kammern - es sind jeweils abhängig von der Flügelzahl mehrere Kammerpaare realisiert - wird nun zur Verdrehung des Rotors bezüglich des Stators und damit zur Winkelverstellung eine Hydraulikflüssigkeit eingepresst oder abgezogen, wozu man sich eines Steuerventils, in der Regel eines 4/3-Wegeventils bedient. An diesem sind Arbeitsanschlüsse A und B vorgesehen, die jeweils zu einer Kammer A und einer Kammer B eines jeweiligen Kammerpaares führen. Das Steuerventil selbst ist bei der in Rede stehenden Nockenwellenverstellerausbildung als Zentralventil ausgebildet, es ist zentral, mittig im Nockenwellenversteller bzw. in dessen Rotor eingesetzt und mit der Nockenwelle verbunden, das heißt, das Steuerventil rotiert also mit dem Versteller bzw. dem Rotor.Known camshaft adjusters are designed, for example, as vane-type adjusters and comprise a rotor which is connected in a rotationally fixed manner to the camshaft and a stator which is coupled to the crankshaft via the timing chain or the timing belt. On the rotor radially outwardly projecting wings are provided which engage between radially inwardly projecting stops on the stator, which on the one hand limit the twisting movement and on the other hand form chamber walls. The chambers are bounded by the respective side of a rotor-side wing and by the sides of the stator-side stops. In these chambers - there are in each case realized depending on the number of blades several pairs of chambers - now a hydraulic fluid is pressed or withdrawn for rotation of the rotor relative to the stator and thus for angular adjustment, including using a control valve, usually a 4/3-way valve , At this working ports A and B are provided, each leading to a chamber A and a chamber B of each chamber pair. The control valve itself is designed as a central valve in the camshaft adjuster configuration in question, it is centrally, inserted centrally in the camshaft adjuster or in its rotor and connected to the camshaft, that is, the control valve rotates with the adjuster or the rotor.

Im Steuerventil selbst ist ein Ventilkolben integriert, der axial beweglich ist, wobei seine Verschiebung über einen zum Nockenwellenversteller extern positionierten, beispielsweise an einem Motor oder sonstigen Drittgegenstand angeordneten Zug- oder Druckmagneten gesteuert wird. Der Magnet ist bei dieser Ausführungsform also nicht im Versteller integriert. Je nach Position des Ventilkolbens wird nun der eine oder andere Arbeitsanschluss A bzw. B mit dem Druckanschluss P gekoppelt, so dass Hydraulikflüssigkeit in die zugeordnete Kammer A oder B geführt wird, während die jeweils andere Kammer mit dem ventilseitigen Ablaufanschluss verbunden wird, so dass die in der entlasteten Kammer befindliche Flüssigkeit über den Ablaufanschluss zum Tank hin abgezogen werden kann. Auf diese Weise kann der Rotor bezüglich des Stators hydraulisch verdreht werden. Zum Halten eines eingestellten Verdrehwinkels zwischen den Anschlägen kann der Ventilkolben beide Arbeitsanschlüsse A und B und damit die zugeordneten Kammern auch nahezu verschließen.In the control valve itself, a valve piston is integrated, which is axially movable, wherein its displacement is controlled by a camshaft adjuster externally positioned, arranged for example on a motor or other third object train or pressure magnet. The magnet is at this Embodiment thus not integrated in the stage. Depending on the position of the valve piston, one or the other working port A or B is now coupled to the pressure port P, so that hydraulic fluid is conducted into the associated chamber A or B, while the respective other chamber is connected to the valve-side drain port, so that the In the unloaded chamber liquid can be withdrawn through the drain port to the tank down. In this way, the rotor can be hydraulically rotated with respect to the stator. To hold a set angle of rotation between the stops of the valve piston can close both working ports A and B and thus the associated chambers and almost.

Bei bekannten Nockenwellenverstellern mit dem in Rede stehenden Steuerventil ist der Druckanschluss P mit der Ventillängsachse fluchtend stirnseitig am Ventilkörper vorgesehen. Die unter Druck zugeführte Hydraulikflüssigkeit drückt gegen eine Stirnfläche des häufig hohlzylindrischen Ventilkolbens, bevor sie je nach Kolbenstellung in den jeweiligen Arbeitsanschluss A oder B übertritt. Dies führt dazu, dass aus der Flüssigkeitszufuhr resultierend eine beachtliche Kraft auf den Kolben ausgeübt wird, die der externe Steuermagnet zur Bewegung des Ventilkolbens in eine entgegengesetzte Richtung überwinden muss. Der Magnetkraft wirkt die auf den Ventilkolben wirkende Feder entgegen, die im stromlosen Zustand des Elektromagneten den Ventilkolben in seine Basisstellung (P - B - A - T) verfährt. Die Feder ist auf das System (Magnetkraft, Strömungs- und Druckkräfte der Hydraulik, Kolbenweg, Kolbenreibung, etc.) abgestimmt. Muss nun zusätzlich auch die flüssigkeitsbedingte, in die entgegengesetzte Richtung wirkende Kraft überwunden werden, kann dies bei hohem anliegenden Flüssigkeitsdruck im Extremfall dazu führen, dass die einwirkende Magnetkraft nicht stark genug ist, den Ventilkolben zu verschieben, bzw. dass der der am Magneten anliegenden elektrischen Leistung zugeordnete Bewegungsweg des Ventilkolbens nicht vollständig zurückgelegt wird. Aus der DE 199 44 535 C1 ist ein Nockenwellenversteller für Brennkraftmaschinen bekannt. Es wird eine Ausbildung des Steuerschiebers vorgeschlagen, die Stellkräfte auf den Steuerschieber durch das über den Steuerschieber laufende Arbeitsmedium verhindert.In known camshaft adjusters with the control valve in question, the pressure port P is provided with the valve longitudinal axis aligned end face on the valve body. The supplied under pressure hydraulic fluid presses against an end face of the often hollow cylindrical valve piston, before it passes depending on the piston position in the respective working port A or B. As a result, a substantial force is exerted on the piston from the fluid supply, which the external control magnet must overcome in order to move the valve piston in an opposite direction. The magnetic force counteracts the spring which acts on the valve piston and moves the valve piston into its basic position (P - B - A - T) when the electromagnet is de - energized. The spring is adapted to the system (magnetic force, hydraulic flow and pressure forces, piston travel, piston friction, etc.). If, in addition, the fluid-related force acting in the opposite direction has to be overcome, this can lead, in the extreme case, to the high pressure applied to the magnetic force not being strong enough to displace the valve piston, or that of the electric current applied to the magnet Power associated movement of the valve piston is not completely covered. From the DE 199 44 535 C1 is known a camshaft adjuster for internal combustion engines. It is proposed an embodiment of the spool valve, which prevents actuating forces on the spool by the current via the spool working fluid.

Zusammenfassung der ErfindungSummary of the invention

Der Erfindung liegt damit das Problem zugrunde, einen Nockenwellenversteller anzugeben, der auch bei hohem anliegenden Flüssigkeitsdruck ein sicheres Stellen des Ventilskolbens zulässt.The invention is therefore based on the problem of specifying a camshaft adjuster, which allows a secure placement of the valve piston even with high applied fluid pressure.

Zur Lösung dieses Problems ist bei einem Nockenwellenversteller der eingangs genannten Art erfindungsgemäß vorgesehen, dass der Flüssigkeitsverteilraum im Steuerventil, also im Ventilkörper bzw. dem Ventilkolben bzw. zwischen diesen beiden, derart ausgeführt ist, dass die Hydraulikflüssigkeit an einander im Wesentlichen entgegengesetzt gerichteten Flächen des Ventilkolbens angreift, so dass auf den Ventilkolben lokale und einander im Wesentlichen entgegengesetzt gerichtete Kräfte wirken.To solve this problem is provided according to the invention in a camshaft adjuster of the type mentioned that the liquid distribution in the control valve, ie in the valve body or the valve piston or between these two, is designed such that the hydraulic fluid at substantially oppositely directed surfaces of the valve piston engages, so act on the valve piston local and each other substantially oppositely directed forces.

Beim erfindungsgemäßen Nockenwellenversteller ist der Flussweg für die Hydraulikflüssigkeit, sobald sie in den Ventilkörper eintritt und bevor sie zu einem der Arbeitsanschlüsse A oder B übertritt, so ausgeführt, dass der Ventilkolben über die Flüssigkeit an zwei einander entgegengesetzt gerichteten Flächen belastet wird, so dass sich aus dieser gerichteten Belastung entgegengesetzt gerichtete, auf den Ventilkolben wirkende Kräfte einstellen, die einander zumindest teilweise kompensieren. Aufgrund dieser Flussführung wird folglich die aus der Flüssigkeitszufuhr resultierende, auf den Ventilkolben einwirkende Gesamtkraft im Vergleich zu den Ausführungen des Standes der Technik deutlich verringert, was dazu führt, dass die vom externen Steuermagneten auf den Ventilkolben bzw. dessen verlängerte Steuerstange, die zum Magneten zeigt, auszuübende Kraft deutlich verringert ist. Damit können sich etwaige Druckspitzen in der Zufuhr der Hydraulikflüssigkeit In keinem Fall nachteilig auf die Ventilsteuerung auswirken.In the camshaft adjuster according to the invention, the flow path for the hydraulic fluid, as soon as it enters the valve body and before it goes to one of the working ports A or B, is designed so that the valve piston is loaded by the fluid at two oppositely directed surfaces, so that out set oppositely directed, directed on the valve piston forces that compensate each other at least partially. As a result of this flow guidance, the total force exerted on the valve piston by the fluid supply is consequently significantly reduced in comparison to the prior art embodiments, which results in that the external control magnet points to the valve piston or its extended control rod pointing towards the magnet , force to be exerted is significantly reduced. Thus, any pressure peaks in the supply of hydraulic fluid can in no case adversely affect the valve control.

Zweckmäßig ist es, wenn die einander entgegengesetzten Kräfte, die durch die erfindungsgemäße Flächenbeaufschlagung erzeugt werden, im Wesentlichen gleichgroß sind, wozu zweckmäßigerweise die beaufschlagten Flächen auch im Wesentlichen gleichgroß sein sollten.It is expedient if the mutually opposite forces which are generated by the Flächenbeaufschlagung invention, are substantially the same size, for which purpose the applied surfaces should also be substantially the same size.

Nach einer ersten Erfindungsausgestaltung kann der Druckanschluss P senkrecht zur Ventilachse liegen und in einen zwischen dem Ventilkolben und dem Ventilkörper gebildeten, stellungsabhängig mit dem Arbeitsanschluss A verbindbaren Ringkanal münden, der in den hohlzylindrischen, an beiden Stirnseiten geschlossenen Ventilkolben führt, dessen Hohlraum stellungsabhängig mit dem Arbeitsanschluss B verbindbar ist, wobei die stirnseitigen Hohlraumflächen über die Hydraulikflüssigkeit mit Druck beaufschlagt werden. Die Flächen, über die die entgegengesetzt gerichteten Kräfte in den Ventilkolben eingebracht werden, sind bei dieser Ausführungsform die den Hohlraum stirnseitig begrenzenden Stirnflächen. Nachdem es sich um ein hohlzylindrisches Kolbenteil mit gleich bleibendem Hohlraumdurchmesser handelt, sind folglich auch die Flächen im Wesentlichen gleichgroß, so dass sich auch im Wesentlichen gleichgroße, entgegengesetzt gerichtete Kräfte einstellen.According to a first embodiment of the invention, the pressure port P can be perpendicular to the valve axis and open into a connected between the valve piston and the valve body, position-dependent connectable to the working port A annular channel which leads into the hollow cylindrical, closed at both ends valve piston, the cavity position-dependent with the working port B is connectable, wherein the frontal cavity surfaces are acted upon by the hydraulic fluid with pressure. The surfaces over which the oppositely directed forces are introduced into the valve piston, in this embodiment, the end faces defining the cavity end face. After it is a hollow cylindrical piston member with a constant cavity diameter, consequently, the surfaces are substantially the same size, so that set also substantially equal, oppositely directed forces.

Bereits an dieser Stelle ist darauf hinzuweisen, dass natürlich - je nach Ausführung des Steuerventils und der Verstellvorrichtung - anstelle des Arbeitsanschlusses A auch der Arbeitsanschluss B mit dem Ringkanal bzw. anstelle des Arbeitsanschlusses B der Arbeitsanschluss A mit dem Hohlraum verbindbar ist, das heißt, die jeweiligen Arbeitsanschlüsse können auch vertauscht werden. Dies gilt für alle nachfolgend beschriebenen Ausführungsformen.Already at this point it should be noted that of course - depending on the design of the control valve and the adjustment - instead of the working port A and the working port B with the annular channel or instead of the working port B of the working port A is connected to the cavity, that is, the respective work connections can also be reversed. This applies to all embodiments described below.

Bei der beschriebenen Ausführungsform kann ferner vorgesehen sein, dass die beiden Arbeitsanschlüsse über einen zwischen dem Ventilkolben und dem Ventilkörper ausgebildeten Ringkanal stellungsabhängig mit dem unter einem Winkel, vorzugsweise senkrecht zur Ventillängsachse liegenden Ablaufanschluss verbindbar sind. Zweckmäßigerweise sind bei dieser Ventilausführung alle Anschlüsse, also sowohl der Druckanschluss P als auch der Ablaufanschluss T und die Arbeitsanschlüsse A und B senkrecht zur Ventilachse verlaufend und in der Reihenfolge B- T- A- P oder A- T- B- P angeordnet, wobei im letztgenannten Fall eine Zugfederr verwendet wird, um das Ventil im stromlosen Zustand, also ohne wirkenden Magneten in die Grundstellung P - B - A - T zu schalten.In the embodiment described, it can further be provided that the two working ports can be connected in a position-dependent manner with the outlet connection situated at an angle, preferably perpendicular to the valve longitudinal axis, via a ring channel formed between the valve piston and the valve body. Conveniently, in this valve design all connections, so both the pressure port P and the drain port T and the working ports A and B perpendicular to the valve axis extending and arranged in the order B- T- A- P or A- T- B- P, wherein In the latter case, a Zugfederr is used to switch the valve in the de-energized state, ie without acting magnet in the basic position P - B - A - T.

Eine Alternativausführung eines Steuerventils sieht vor, dass der Druckanschluss P unter einem Winkel, vorzugsweise senkrecht zur Ventilachse liegt und in einen zwischen dem Ventilkolben und dem Ventilkörper gebildeten stellungsabhängig mit dem Arbeitsanschluss A oder B verbindbaren Ringraum mündet, wobei die Arbeitsanschlüsse A, B stellungsabhängig über Verbindungsbohrungen mit dem Hohlraum des hohlzylindrischen Ventilkolbens verbindbar sind, welcher Hohlraum zum Ablaufanschluss T führt, der bei dieser Ausführungsform axial mit der Ventillängsachse fluchtend verläuft. Auch hier können zweckmäßigerweise der Druckanschluss P und die Arbeitsanschlüsse A und B senkrecht zur Ventillängsachse verlaufen und in der Reihenfolge A- P - B angeordnet sein.An alternative embodiment of a control valve provides that the pressure port P is at an angle, preferably perpendicular to the valve axis and opens in a formed between the valve piston and the valve body position-dependent connectable to the working port A or B annulus, wherein the working ports A, B position-dependent via connecting holes can be connected to the cavity of the hollow cylindrical valve piston, which cavity leads to the drain port T, which in this embodiment is axially aligned with the valve longitudinal axis. Here too, expediently, the pressure port P and the working ports A and B can run perpendicular to the longitudinal axis of the valve and be arranged in the order A-P-B.

Eine weitere Ausführungsvariante sieht vor, dass der Druckanschluss P in der Ventillängsachse liegt und über Umlenkkanäle in einen zwischen dem Ventilkolben und dem Ventilkörper gebildeten, stellungsabhängig mit dem Arbeitsanschluss A oder B verbindbaren Ringraum mündet, wobei die Arbeitsanschlüsse A, B stellungsabhängig über Verbindungsbohrungen mit dem Hohlraum des hohlzylindrischen Ventilkolbens verbindbar sind, welcher Hohlraum zum Ablaufanschluss T führt.A further embodiment provides that the pressure port P is located in the valve longitudinal axis and opens via deflecting channels formed in a position-dependent connected to the working port A or B annular space between the valve piston and the valve body, wherein the working ports A, B position-dependent via connecting holes with the cavity the hollow cylindrical valve piston can be connected, which leads cavity to the drain port T.

Schließlich sieht eine weitere Ventilausführungsform vor, dass der Druckanschluss P mit der Ventillängsachse fluchtend verläuft und in den hohlzylindrischen Ventilkolben mündet, an dem radiale Öffnungen vorgesehen sind, durch die die Hydraulikflüssigkeit in den zwischen dem Ventilkolben und dem Ventilkörper gebildeten Ringraum gelangt, der von der Stirnseite des Ventilkolbens begrenzt ist. Bei dieser Ausführungsform wird- ähnlich wie im Stand der Technik- die Hydraulikflüssigkeit axial in den hohlzylindrischen Ventilkolben geführt. Infolge der erfindungsgemäß vorgesehenen Kolbenöffnungen tritt die Flüssigkeit aus dem Kolben in den hinteren, zwischen dem Kolben und dem Ventilkörper gebildeten Ringraum ein, wo sie quasi umgelenkt wird und auf die entgegengesetzt zur Hohlraumstirnwand liegende Kolbenaußenfläche drückt. Auch bei dieser Ausführungsform werden also einander quasi entgegengesetzt gerichtete Flächen beaufschlagt, so dass entgegengesetzt gerichtete lokale Kräfte auf den Ventilkolben wirken.Finally, another valve embodiment provides that the pressure port P is aligned with the valve longitudinal axis and opens into the hollow cylindrical valve piston, are provided at the radial openings through which the hydraulic fluid passes into the annular space formed between the valve piston and the valve body, from the front side the valve piston is limited. In this embodiment, similar to the prior art, the hydraulic fluid is guided axially into the hollow cylindrical valve piston. As a result of the inventively provided piston openings, the liquid from the piston enters the rear, formed between the piston and the valve body annulus, where it is virtually deflected and presses on the opposite opposite to the cavity end wall piston outer surface. Also in this embodiment, therefore, are virtually opposite each other directed surfaces acted so that oppositely directed local forces act on the valve piston.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Fig. 1Fig. 1
zeigt eine Schnittansicht eines Steuerventils einer ersten Ausfüh- rungsform,shows a sectional view of a control valve of a first embodiment,
Fig. 2Fig. 2
zeigt einen erfindungsgemäßen Nockenwellenversteller mit dem integrierten Steuerventil aus Fig. 1,shows a camshaft adjuster according to the invention with the integrated control valve Fig. 1 .
Fig. 3 zeigtFig. 3 shows
einen erfindungsgemäßen Nockenwellenversteller einer zweiten Ausführungsform mit einem integrierten Steuerventil einer zweiten Ausführungsform,a camshaft adjuster according to the invention of a second embodiment with an integrated control valve of a second embodiment,
Fig. 4Fig. 4
zeigt ein Steuerventil einer dritten Ausführungsform, undshows a control valve of a third embodiment, and
Fig. 5Fig. 5
zeigt ein Steuerventil einer vierten Ausführungsform.shows a control valve of a fourth embodiment.
Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

Fig. 1 zeigt ein Steuerventil 1 bestehend aus einem Ventilkörper 2, an dem im gezeigten Ausführungsbeispiel ein Außengewinde 3 vorgesehen ist, über das der Ventilkörper nach Einsetzen in den Rotor einer Verstelleinrichtung nockenwellenseitig verschraubt wird. Im Ventilkörper 2 ist ein Ventilkolben 4 axial beweglich geführt, der gegen eine von einer Feder 5 erzeugte Rückstellkraft bewegt werden kann. Zur Bewegung ist am Ventilkolben 4 eine Stößelstange 6 angeordnet, die mit einem externen, nicht näher gezeigten Steuermagneten zusammenwirkt, um den Ventilkolben gegen die Feder oder mit Federunterstützung in die andere Richtung zu bewegen. Der Steuermagnet ist wie beschrieben extern beispielsweise am Motor angeordnet, er bewegt sich also nicht, anders als das Steuerventil 1, das mit dem Rotor dreht. Das Steuerventil 1 ist im Gehäuse des Nockenwellenverstellers gekapselt aufgenommen, über welches Gehäuse die Stößelstange 6 mit dem Magneten zusammenwirkt. Fig. 1 shows a control valve 1 consisting of a valve body 2, on which in the illustrated embodiment, an external thread 3 is provided, via which the valve body is screwed camshaft side after insertion into the rotor of an adjustment. In the valve body 2, a valve piston 4 is guided axially movable, which can be moved against a restoring force generated by a spring 5. For movement, a push rod 6 is arranged on the valve piston 4, which cooperates with an external control magnet, not shown in detail, to move the valve piston against the spring or with spring support in the other direction. The control magnet is as described externally arranged for example on the engine, so it does not move, unlike the control valve 1, which rotates with the rotor. The control valve 1 is enclosed encapsulated in the housing of the camshaft adjuster, via which housing the push rod 6 cooperates with the magnet.

Am Ventilkörper 2 sind mehrere unterschiedliche Anschlüsse vorgesehen. Zum einen ist ein Arbeitsanschluss A sowie ein Arbeitsanschluss B gezeigt, über die eine Hydraulikflüssigkeit in entsprechende Kammern der als Flügelzellen-Verstellvorrichtung ausgebildeten Vorrichtung gefördert werden kann, abhängig von der Stellung des Ventilkolbens 4. Gezeigt ist ferner ein Druckanschluss P, über den von einer nicht näher gezeigten Pumpe die Hydraulikflüssigkeit zugeführt wird. Ferner ist ein Ablaufanschluss T gezeigt, über den abzuführende Hydraulikflüssigkeit in einen nicht näher gezeigten Tank gefördert wird.On the valve body 2 several different connections are provided. On the one hand, a working port A and a working port B are shown, via which a hydraulic fluid can be conveyed into corresponding chambers of the device designed as a vane-cell adjusting device, depending on the position of the valve piston 4. Also shown is a pressure port P, not one of them pump shown in detail, the hydraulic fluid is supplied. Further, a drain port T is shown, is conveyed via the discharged hydraulic fluid in a tank not shown in detail.

Am Ventilkolben 4 sind verschiedene Steuerkanten 7a (die dem Arbeitsanschluss A zugeordnet sind) sowie 7b (die dem Arbeitsanschluss B zugeordnet sind) vorgesehen. Über diese Steuerkanten werden je nach Stellung des Ventilkolbens die Arbeitsanschlüsse A und B entweder mit dem Druckanschluss P oder dem Ablaufanschluss T über den Kanal 41 verbunden, je nachdem, ob in die Kammern, die dem Arbeitsanschluss A zugeordnet sind, Flüssigkeit zugeführt und aus den Kammern, die dem Arbeitsanschluss B zugeordnet sind, Flüssigkeit abgeführt und in den Tank über den Ablaufanschluss T gefördert werden sollen, oder umgekehrt. Die Stellung wird über den nicht näher gezeigten Magneten gesteuert.On the valve piston 4, various control edges 7a (which are assigned to the working port A) and 7b (which are assigned to the working port B) are provided. Depending on the position of the valve piston, the working ports A and B are connected via these control edges either to the pressure port P or to the discharge port T via the channel 41, depending on whether fluid is supplied into the chambers, which are assigned to the working port A, and out of the chambers , which are assigned to the working port B, liquid to be discharged and conveyed into the tank via the drain port T, or vice versa. The position is controlled by the magnet not shown in detail.

Um zu vermeiden, dass durch die mit relativ hohem Druck zugeführte Hydraulikflüssigkeit eine Kraft auf den Ventilkolben ausgeübt wird, die vom Magneten, der zum Bewegen des Ventilkolbens 4 entgegen der Federkraft bewegt wird, zusätzlich zu überwinden wäre, ist bei dem Steuerventil 1 ein Ringkanal 8 vorgesehen, in den der Druckanschluss P mündet. Über ventilkolbenseitige Öffnungen 9 mündet der Ringkanal 8- der je nach Kolbenstellung im Bedarfsfall mit dem Arbeitsanschluss A verbunden werden kann- in den Hohlraum 10 des Ventilkolbens 4. Über entsprechende Öffnungen 11 ist der Hohlraum 10 je nach Kolbenstellung mit dem Arbeitsanschluss B verbindbar, wenn diesem die Hydraulikflüssigkeit zugeführt werden soll.In order to avoid that by the supplied with relatively high pressure hydraulic fluid, a force is exerted on the valve piston, which would be overcome by the magnet, which is moved to move the valve piston 4 against the spring force, in addition to be in the control valve 1, an annular channel. 8 provided in the pressure port P opens. About valve-piston-side openings 9 of the annular channel opens 8- depending on the piston position in case of need to be connected to the working port A- in the cavity 10 of the valve piston 4. Via corresponding openings 11, the cavity 10 depending on the piston position with the working port B connectable, if this the hydraulic fluid to be supplied.

Die Hydraulikflüssigkeit drückt im Hohlraum 10 auf zwei einander entgegengesetzte Stirnflächen 12, 13, die den Hohlraum axial gesehen begrenzen. Hieraus resultiert eine auf den Ventilkolben jeweils gerichtet wirkende Kraft Fp1 bzw. Fp2, die ersichtlich einander entgegengesetzt gerichtet sind. Die beiden Kräfte- die im Idealfall gleichgroß sind- kompensieren also einander, so dass der Ventilkolben 4 im Idealfall quasi drucklos ist, soweit Kräfte auf ihn über die Flüssigkeitszufuhr wirken.The hydraulic fluid presses in the cavity 10 on two opposite end faces 12, 13, which limit the cavity seen axially. This results in a force F p1 or F p2 directed in each case on the valve piston, which are obviously directed opposite to one another. The two forces - which are ideally equal in the ideal case - thus compensate each other, so that the valve piston 4 in the ideal case virtually quiescent, as far as forces acting on him on the liquid supply.

Fig. 2 zeigt einen erfindungsgemäßen Nockenwellenversteller 14, mit einem Rotor 15 und einem Stator 16. Der Rotor 15 ist drehfest mit dem Steuerventil 1 verbunden, diese Mimik ist bezüglich des Stators 16, der mit der Steuerkette oder dem Steuerriemen mit der Kurbelwelle verbunden ist, drehbeweglich. Bekanntlich sind am Rotor mehrere Flügel 17 vorgesehen, die dicht an der Innenwand 18 des Stators anliegen und über die jeweils zwei Kammern begrenzt werden, die jeweils über einen Arbeitsanschluss A bzw. B mit Fluid beaufschlagt bzw. von dort über die jeweiligen Arbeitsanschlüsse Fluid abgezogen werden kann. Ein näheres Eingehen hierauf ist nicht erforderlich, nachdem der grundsätzliche Aufbau derartiger Nockenwellenversteller hinlänglich bekannt ist. Fig. 2 shows a camshaft adjuster 14 according to the invention, with a rotor 15 and a stator 16. The rotor 15 is rotatably connected to the control valve 1, this mimic is rotatable with respect to the stator 16 which is connected to the timing chain or the timing belt with the crankshaft. As is known, a plurality of vanes 17 are provided on the rotor, which bear tightly against the inner wall 18 of the stator and are bounded by the respective two chambers, which are each acted upon via a working port A or B with fluid or withdrawn from there via the respective working fluid connections can. A closer approach to this is not required after the basic design of such camshaft adjuster is well known.

Fig. 3 zeigt eine weitere erfindungsgemäße Ausführungsform eines Nockenwellenverstellers 19, der vom grundsätzlichen Aufbau her dem Nockenwellenversteller 14 aus Fig. 2 entspricht, jedoch ist das integrierte Steuerventil 20 anders aufgebaut. Es weist ebenfalls einen P-Druckanschluss sowie die beiden Arbeitsanschlüsse A und B wie auch einen Ablaufanschluss T auf. Jedoch liegt hier der Druckanschluss P, der von außen über den Ventilkörper 21 nach innen geführt wird, quasi mittig zwischen den Arbeitsanschlüssen A und B, die über die Stellung des Ventilkolbens 22 in entsprechender Weise wie bezüglich des Steuerventils 1 beschrieben mit dem Druckanschluss P bzw. dem Ablaufanschluss T, der hier axial mit der Ventillängsachse verläuft, verbindbar sind. Auch bei dieser Ausführungsform, bei der der Ventilkolben 22 ebenfalls über einen nicht näher gezeigten Steuermagneten gegen eine nicht näher gezeigte Rückstellfeder bewegbar ist, erfolgt die Flüssigkeitszufuhr derart, dass auf den Ventilkolben 22 einander weitgehend kompensierende, aus der eingepressten Flüssigkeit resultierende Kräfte wirken. Der Druckanschluss P mündet in einen Ringkanal 23, der von den Steuerflanken 24, 25, über die die Verbindung zu den Arbeitsanschlüssen A bzw. B geöffnet oder geschlossen werden, begrenzt ist. Die Flüssigkeit drückt also auf diese einander entgegengesetzt gerichteten Flanken, so dass sich zwangsläufig entgegengesetzt gerichtete Kräfte einstellen, die einander kompensieren. Auch hier ist also ein Flüssigkeitsverteilraum realisiert, der eine Kräftekompensation zulässt. Fig. 3 shows a further embodiment according to the invention a camshaft adjuster 19, the basic structure of the camshaft adjuster 14 from Fig. 2 corresponds, but the integrated control valve 20 is constructed differently. It also has a P-pressure port and the two working ports A and B as well as a drain port T. However, here lies the pressure port P, which is guided from the outside via the valve body 21 inwardly, quasi-centered between the working ports A and B, which via the position of the valve piston 22 in a corresponding manner as described with respect to the control valve 1 with the pressure port P or the drain port T, which runs axially here with the valve longitudinal axis, are connectable. Also in this embodiment, in which the valve piston 22 also via a control magnet not shown in detail against a not shown in detail Return spring is movable, the liquid is supplied in such a way that on the valve piston 22 substantially compensating each other, resulting from the pressed liquid forces act. The pressure port P opens into an annular channel 23 which is bounded by the control flanks 24, 25, via which the connection to the working ports A and B are opened or closed. The liquid thus presses on these oppositely directed flanks, so that inevitably set oppositely directed forces that compensate each other. Here, too, a liquid distribution space is realized, which allows a compensation of forces.

Schließlich zeigt Fig. 4 ein weiteres Steuerventil 26, das gleichermaßen in einen Nockenwellenversteller wie er in den vorangehenden Figuren gezeigt ist integriert werden kann. Auch dieses Steuerventil weist einen Ventilkörper 27 und einen Ventilkolben 28 auf. Der Druckanschluss P liegt hier axial zur Ventillängsachse, während die nicht näher gezeigten Arbeitsanschlüsse A und B sowie der Ablaufanschluss T vertikal zur Ventillängsachse liegen.Finally shows Fig. 4 another control valve 26, which can be integrated equally into a phaser as shown in the preceding figures. This control valve also has a valve body 27 and a valve piston 28. The pressure port P is here axially to the valve longitudinal axis, while the working ports A and B, not shown in detail and the drain port T are vertical to the valve longitudinal axis.

Ersichtlich ist auch hier der Ventilkolben gegen eine Rückstellfeder 29 gelagert. Er ist hohlzylindrisch, die zugeführte Flüssigkeit tritt in ihn ein. An der gegenüberliegenden Seite sind jedoch mehrere Öffnungen 30 vorgesehen, so dass die Flüssigkeit in den dieses Kolbenende umgebenden Ringraum 31 eintreten kann. Dort drückt die Flüssigkeit auf die Kolbenaußenfläche 32, die der Stirnfläche 33 im Inneren des Kolbens gegenüberliegt. Auch hier werden also wieder zwei einander entgegengesetzt gerichtete Flächen mit dem Fluid beaufschlagt, so dass sich einander entgegengesetzt gerichtete Kräfte ergeben, die auf den Ventilkolben 28 einwirken.Obviously, the valve piston is mounted against a return spring 29 here. It is hollow cylindrical, the liquid supplied enters it. On the opposite side, however, a plurality of openings 30 are provided, so that the liquid can enter the surrounding this piston end annular space 31. There, the liquid presses on the piston outer surface 32, which faces the end face 33 in the interior of the piston. Again, two oppositely directed surfaces are thus again subjected to the fluid, so that mutually oppositely directed forces arise, which act on the valve piston 28.

Schließlich zeigt Fig. 5 ein weiteres erfindungsgemäßes Steuerventil 34, dessen Druckanschluss P ebenfalls axial verläuft, die Arbeitsanschlüsse A und B gehen am Ventilkörper 35 senkrecht zur Längsachse ab, während der Ablaufanschluss T aus dem Ventilkolben 36 vertikal zur Längsachse abgeht. Auch hier wird die Hydraulikflüssigkeit über entsprechende Führungskanäle 37 zunächst umgelenkt und anschließend in einen Ringraum 38 gegeben, der von zwei Flächen 39, 40 am Ventilkolben 36 begrenzt ist. Diese Ausführungsform entspricht im Wesentlichen der Ventilausführung aus Fig. 3, es stellen sich auch hier gleichgroße, jedoch entgegengesetzt gerichtete Kräfte am Ventilkolben 36 ein. Jedoch ist hier die Zufuhr der Hydraulikflüssigkeit axial, während sie beim Ventil in Fig. 3 von der Seite her erfolgt.Finally shows Fig. 5 a further control valve 34 according to the invention, whose pressure port P also extends axially, the working ports A and B are on the valve body 35 perpendicular to the longitudinal axis, while the drain port T from the valve piston 36 is vertical to the longitudinal axis. Again, the hydraulic fluid is first deflected via corresponding guide channels 37 and then placed in an annular space 38, the of two surfaces 39, 40 is limited to the valve piston 36. This embodiment substantially corresponds to the valve design Fig. 3 , There are also here equal, but oppositely directed forces on the valve piston 36 a. However, here is the supply of hydraulic fluid axially, while the valve in Fig. 3 done from the side.

Bezugszahlenreference numerals

11
Steuerventilcontrol valve
22
Ventilkörpervalve body
33
Außengewindeexternal thread
44
Ventilkolbenplunger
55
Federfeather
66
Stößelstangepushrod
7a, 7b7a, 7b
Steuerkantencontrol edges
88th
Ringkanalannular channel
99
Öffnungenopenings
1010
Hohlraumcavity
1111
Öffnungenopenings
1212
Stirnflächenfaces
1313
Stirnflächenfaces
1414
NockenwellenvenstellerNockenwellenvensteller
1515
Rotorrotor
1616
Statorstator
1717
Flügelwing
1818
Innenwandinner wall
1919
NockenwellenverstellerPhaser
2020
Steuerventilcontrol valve
2121
Ventilkörpervalve body
2222
Ventilkolbenplunger
2323
Ringkanalannular channel
2424
Steuerflankencontrol edges
2525
Steuerflankencontrol edges
2626
Steuerventilcontrol valve
2727
Ventilkörpervalve body
2828
Ventilkolbenplunger
2929
RückstellfederReturn spring
3030
Öffnungenopenings
3131
Ringraumannulus
3232
KolbenaußenflächeOuter piston surface
3333
Stirnflächeface
3434
Steuerventilcontrol valve
3535
Ventilkörpervalve body
3636
Ventilkolbenplunger
3737
Führungskanäleguide channels
3838
Ringraumannulus
3939
Flächensurfaces
4040
Flächensurfaces
4141
Kanalchannel
AA
Arbeitsanschlussworking port
BB
Arbeitsanschlussworking port
PP
Druckanschlusspressure connection
TT
Ablaufanschlussdrain connection
Fp1 F p1
Kraftforce
Fp2 F p2
Kraftforce

Claims (5)

  1. Camshaft adjuster for relative angle adjustment of a camshaft with respect to a driving crankshaft, having a hydraulically operable adjustment apparatus with chambers into which and from which a hydraulic fluid can be supplied and carried away alternately for angle adjustment of the chamber-specific pressure-medium channels, and having a control valve (1), which is integrated centrally in the adjustment apparatus, and rotates with it, via which the hydraulic fluid, which is supplied via a pump, can be supplied to the pressure-medium channels and can be carried away from the pressure-medium channels into a tank, with operating connections A and B, which lead to the pressure-medium channels, a pressure connection P which can be coupled to the pump, and an outlet connection T which can be coupled to the tank being provided on the valve body (2) of the control valve (1), which operating connections A and B can be selectively coupled to the pressure connection P or to the outlet connection T, depending on the angle adjustment required, via a valve piston (4) which can be moved in a controlled manner via a decoupled pulling or pushing magnet which is arranged externally with respect to the camshaft adjuster, the fluid distribution area in the control valve (1) being designed in such a manner that the hydraulic fluid acts on surfaces of the valve piston (4) which point essentially in mutually opposite direction, so that local forces (Fp1, Fp2), which are essentially in opposite directions to one another, act on the valve piston (4), characterized in that the pressure connection P is at an angle, preferable at right angles, to the valve axis and opens into an annular channel (8) which is formed between the valve piston (4) and the valve body (2), can be connected to the operating connection A as a function of position, and leads into the hollow-cylindrical valve piston (4), which is closed at both ends and whose cavity (10) can be connected as a function of position to the operating connection B, with pressure being applied to the end cavity surfaces (12, 13) via the hydraulic fluid.
  2. Camshaft adjuster according to Claim 1, characterized in that the two operating connections A, B can be connected as a function of position to the outlet connection T, which is at right angles to the valve longitudinal axis, via an annular channel (41) which is formed between the valve piston (4) and the valve body (2).
  3. Camshaft adjuster according to Claim 1 or 2, characterized in that the pressure connection P, the outlet connection T and the operating connections A and B are arranged running at right angles to the valve longitudinal axis and in the sequence B-T-A-P, or A-T-B-P.
  4. A camshaft adjuster for relative angle adjustment of a camshaft with respect to a driving crankshaft, having a hydraulically operable adjustment apparatus with chambers into which and from which a hydraulic fluid can be supplied and carried away alternately for angle adjustment of the chamber-specific pressure-medium channels, and having a control valve (26), which is integrated centrally in the adjustment apparatus, and rotates with it, via which the hydraulic fluid, which is supplied via a pump, can be supplied to the pressure-medium channels and can be carried away from the pressure-medium channels into a tank, with operating connections A and B, which lead to the pressure-medium channels, a pressure connection P which can be coupled to the pump, and an outlet connection T which can be coupled to the tank being provided on the valve body (27) of the control valve (26), which operating connections A and B can be selectively coupled to the pressure connection P or to the outlet connection T, depending on the angle adjustment required, via a valve piston which can be moved in a controlled manner via a decoupled pulling or pushing magnet which is arranged externally with respect to the camshaft adjuster, characterized in that the fluid distribution area in the control valve (26) is designed in such a manner that the hydraulic fluid acts on surfaces of the valve piston (28) which point essentially in mutually opposite directions, so that local forces (Fp1, Fp2), which are essentially in opposite directions to one another, act on the valve piston (28), characterized in that the pressure connection P runs aligned with the valve longitudinal axis and opens into the hollow-cylindrical valve piston (28) on which radial openings (30) are provided through which the hydraulic fluid enters the annular space (31) which is formed between the valve piston (28) and the valve body (27) and is bounded by the end face of the valve piston (28).
  5. Camshaft adjuster according to one of the preceding claims, characterized in that the mutually opposite forces (Fp1, Fp2) are essentially of equal magnitude.
EP05737740A 2004-05-22 2005-05-04 Camshaft adjuster Active EP1749146B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004025215A DE102004025215A1 (en) 2004-05-22 2004-05-22 Phaser
PCT/EP2005/004849 WO2005113943A1 (en) 2004-05-22 2005-05-04 Camshaft adjuster

Publications (2)

Publication Number Publication Date
EP1749146A1 EP1749146A1 (en) 2007-02-07
EP1749146B1 true EP1749146B1 (en) 2011-04-27

Family

ID=34966090

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05737740A Active EP1749146B1 (en) 2004-05-22 2005-05-04 Camshaft adjuster

Country Status (4)

Country Link
US (1) US20070169730A1 (en)
EP (1) EP1749146B1 (en)
DE (2) DE102004025215A1 (en)
WO (1) WO2005113943A1 (en)

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DE102005034275B4 (en) 2005-07-22 2018-02-15 Daimler Ag Camshaft variable valve mechanism
DE102007020525A1 (en) * 2007-05-02 2008-11-06 Schaeffler Kg Camshaft adjuster for an internal combustion engine with integrated valve slide
DE102007058491A1 (en) * 2007-12-05 2009-06-10 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102009022930A1 (en) 2009-05-27 2010-12-02 Schaeffler Technologies Gmbh & Co. Kg Engaging unit for use in rotational angle limitation device utilized in internal-combustion engine, has stopper provided at supporting and engaging elements that are partially engaged into cavities of other elements
DE102010002713B4 (en) * 2010-03-09 2013-12-05 Schwäbische Hüttenwerke Automotive GmbH Camshaft phaser with control valve for the hydraulic adjustment of the phasing of a camshaft
DE102010023864B4 (en) 2010-06-15 2018-03-08 Hilite Germany Gmbh Central valve for a Schwenkmotornockenwellenversteller
DE102010044637A1 (en) * 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Oscillating motor cam shaft adjuster has housing with hollow piston displaceable axially within housing, where borehole leads to recess that is exclusively assigned in hollow piston
US8695548B2 (en) 2010-12-10 2014-04-15 Denso Corporation Valve timing control apparatus
WO2013174533A1 (en) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Control valve of a camshaft adjuster
DE102014200462A1 (en) * 2014-01-14 2015-01-08 Schaeffler Technologies Gmbh & Co. Kg Phaser
DE102014207989A1 (en) 2014-04-29 2015-10-29 Schaeffler Technologies AG & Co. KG Hydraulic phaser of a camshaft
DE102014214251B4 (en) 2014-07-22 2017-09-14 Schaeffler Technologies AG & Co. KG Hydraulic phaser of a camshaft
DE102014223995A1 (en) 2014-11-25 2016-05-25 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster

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DE3937644A1 (en) * 1989-11-11 1991-05-16 Bayerische Motoren Werke Ag IC engine camshaft hydraulic rotary angle adjuster - has locking device securing vaned wheel in initial angular position w.r.t. sliding vane wheel
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Also Published As

Publication number Publication date
US20070169730A1 (en) 2007-07-26
WO2005113943A1 (en) 2005-12-01
DE502005011305D1 (en) 2011-06-09
EP1749146A1 (en) 2007-02-07
DE102004025215A1 (en) 2005-12-08

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