EP2905434B1 - Oscillating-camshaft phaser having a hydraulic valve - Google Patents
Oscillating-camshaft phaser having a hydraulic valve Download PDFInfo
- Publication number
- EP2905434B1 EP2905434B1 EP14198646.3A EP14198646A EP2905434B1 EP 2905434 B1 EP2905434 B1 EP 2905434B1 EP 14198646 A EP14198646 A EP 14198646A EP 2905434 B1 EP2905434 B1 EP 2905434B1
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- EP
- European Patent Office
- Prior art keywords
- connector
- working
- pressure
- tank
- hydraulic valve
- 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.)
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- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 title description 3
- 241000251730 Chondrichthyes Species 0.000 claims description 3
- 239000012530 fluid Substances 0.000 description 20
- 239000003921 oil Substances 0.000 description 18
- 230000003993 interaction Effects 0.000 description 10
- 230000000903 blocking effect Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000003716 rejuvenation Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 238000004091 panning Methods 0.000 description 1
- 230000003449 preventive effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
-
- 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
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/01—Absolute values
Definitions
- the invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve having two working ports.
- the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already relate to a Schwenkmotornockenwellenversteller with a hydraulic valve having two working ports. These two working ports each have axially adjacent to each other a standard opening and an opening for utilizing pressure peaks due to camshaft alternating torques.
- a hydraulic pressure can be conducted from a supply connection to the work connection to be loaded, while the work connection to be relieved is guided to a tank connection.
- the hydraulic valve is designed as a multi-port multi-position valve in cartridge design. In the carrier or central pin check valves are used on the inside, which are designed as band-shaped rings.
- camshaft alternating torques are used to adjust the camshaft adjuster faster or with a relatively low oil pressure can.
- the check valves open to utilize pressure spikes due to camshaft alternating torques and obscure the backflow preventive ports into the unloaded port.
- the second working port B associated pressure chambers 5 are relieved.
- the second working port B is performed in switch position 19 via a tank connection T to a tank 20.
- the pressure chambers 6 are acted upon by the first working port A coming from the supply port P pressure, but the second working port B is blocked against the tank port T.
- switching position 7b is a connection of the supply port P with the first working port A, while the second working port B is blocked against the tank port T.
- switching position 7b prevents interaction between the inner web of the piston with the web of the cartridge or the central valve pin, that the second working port B is open to the supply port P. Therefore, in the switching position 7b, it is prevented that the second working port B is opened to both the tank port T and the supply port P.
- the switch positions 7a and 7b offer the advantage that the adjuster remains completely filled with oil at lower pump pressures. By blocking a working port against the supply port P, the supply port P can better fill the other working port.
- the adjustment of the camshaft is accomplished by loading one side of the vanes by utilizing recirculated oil available as a result of camshaft alternating torques, in conjunction with oil supplied from the supply port P.
- pressure from the other side of the vanes is relieved only by returning oil to the loaded vanes.
- one of the first working port A is assigned in shift position 15
- a hydraulic fluid volume flow coming from a check valve RSV-B assigned to the second working port B is made available to the supply port P and A. In switching positions 15 and 16, however, no connection of any connection with the tank 20 is made.
- FIG. 4 to FIG. 10 show exemplary structural embodiments of the hydraulic valve 3 in the seven switching positions 18, 15, 7a, 7, 7b, 16, 19 according to Fig. 1 ,
- FIG. 4 shows the hydraulic valve 3 in the first switching position 18, in which the electromagnet 17 according to Fig. 1 a piston 22 of the hydraulic valve 3 does not move.
- the stroke of the piston 22 is thus at zero.
- the piston 22 is within a central bolt 27 against the force of as Helical compression spring running spring 21 slidably.
- the electromagnet 17 facing the end 50 of the piston 22 is closed to produce a contact surface for an actuating plunger of the electromagnet 17, whereas the other end 52 of the piston 22 for receiving one end of the spring 21 is open.
- the piston 22 is held in the central bolt 27 via a retaining ring 54.
- the piston 22 has at its two ends outer webs 23, 24, which are guided relative to the central pin 27.
- the two outer webs 23, 24 have partially over the webs flat flow surfaces 29, 30, so that along these flow surfaces 29, 30 from the ends of the central bolt 27 access to the tank port T is present.
- the piston 22 is hollow and that axial connection bores for flow to the tank connection T are contained.
- two narrow ribs or webs 31, 32 are provided, which run around the piston 22.
- These circumferential ribs 31, 32 correspond to two annular webs 33, 34 extending radially inwardly from the central pin 27.
- two axially outer annular webs 35, 36 are provided.
- These four ring lands 33, 34, 35, 36 are formed by five inner ring grooves 37, 38, 39, 40, 41 are hollowed out of the central pin 27.
- this five réelleringnuten 37, 38, 39, 40, 41 open five connecting holes 60, 62, 64, 66, 68, which are drilled through the wall of the central pin 27. Depending on the flow requirements more than one hole per ring groove are possible.
- connection bores 60, 62, 64, 66, 68 form from the sides of the electromagnet 17 axially along the Bolt 27 comprises: a standard opening B associated with the second working port B, an opening B1 associated with the second working port B for utilizing camshaft alternating torques, the supply port P, an opening A1 associated with the first working port A, and an opening A associated with the first working port A for the use of camshaft alternating torques.
- the band-shaped pump check valve RSV-P is still provided in an inner ring groove 39.
- the pump check valve RSV-P has basically the same structure as the two check valves RSV-A, RSV-B. However, this pump check valve RSV-P may have a different response force.
- the two central ribs 31, 32 are axially spaced from the two annular ribs 33, 34, so that hydraulic fluid can pass through the gap therebetween.
- hydraulic fluid can pass through the gap between the foremost outer web 23 and the corresponding annular web 35 on the central pin 27.
- the other outer bar 24 blocks the rearmost inner annular groove 41 or the standard opening A associated with the first working port A.
- the outer bar 24 and the rearmost annular bar 36 overlap over a large sealing length.
- the first working port A is increasingly opened to the tank port T. This allows both hydraulic fluid return from the first working port A to the second working port B and guiding the first working port A to the tank (that is, hydraulic fluid flow from the first working port A to the tank port T).
- FIG. 7 shows the piston 22 at a stroke of 1.7 mm.
- the hydraulic valve 3 is in the locking middle position 7.
- the supply port P is closed by the two ribs 31, 32.
- the corresponding annular ridges 33, 34 in a correspondingly large extent.
- the two working ports A, B are blocked due to the interaction of web 24 with the surface 98 and the interaction of web 23 with the surface 99 and against the tank drain T.
- FIG. 7 shown locking middle position 7 is practically the holding position
- the piston between this switching position and either the in FIG. 6 shown switching position 7a or in FIG. 8 move shown switching position 7b to compensate for hydraulic fluid leakage.
- FIG. 9 shows the piston 22 at a stroke of 3.0 mm.
- the hydraulic valve 3 is in the switching position 16, and the second working port B is blocked by the interaction of web 23 with the surface 99 against the tank port T. Furthermore, short-term peak pressures are transmitted from the second working port B associated opening B1 through its check valve RSV-B due to the camshaft alternating torques.
- the first working port A is pressurized by the supply port P, and pressure from the second working port B is returned (via port B1) from B to A.
- FIG. 10 shows the piston 22 at a stroke of 3.4 mm.
- this switching position 19 the two middle ribs 31, 32 axially spaced from the two annular ridges 33, 34, so that hydraulic fluid can pass through the gaps between them.
- hydraulic fluid can pass through the gap between the rearmost outer web 24 and the corresponding annular web 36.
- the other outer web 23 blocks the foremost inner annular groove 37 or the standard opening B associated with the second working port B.
- the outer web 23 and the foremost annular web 35 overlap over a large sealing length. This can be done in This switching position 19 hydraulic fluid from the supply port P via the pump check valve RSV-P to the first working port A associated standard opening A arrive.
- the second working port B is increasingly opened to the tank port T. This allows both hydraulic fluid return from the second working port B to the first working port A and guiding the second working port B to the tank (that is, hydraulic fluid flow from the second working port B to the tank port T).
- the duty cycle (or current) may be limited to allowing feedback only (switch positions 15 and 16) when there is adequate cam torque to achieve desired phase rates , It may also be limited to the switch positions 15 and 16 when insufficient current is present in the engine oil system and further loading is undesirable.
- the software allows the use of the shift positions 18 and 19 for phasing. High revolutions per minute also do not allow enough time to make good use of cam torque pulses, thus utilizing switch positions 18 and 19 can increase phase-up speeds at high revolutions per minute, if required.
- the amount of flow opening to the tank port T and the valve lift positions in which the shift positions 18 and 19 begin can be tailored to the application.
- the standard opening A or B and the opening A1 or B1 are combined to initially utilize camshaft alternating moments outside of the central pin 27 to the working port A and B, respectively.
- ball check valves may be used instead of tape check valves.
- the hydraulic valve ball check valves such as the DE 10 2007 012 967 B4 shows.
- the ball check valves need not necessarily be installed in the central valve of a cartridge valve. It is also possible, for example, to use ball check valves in a rotor and to perform the piston as a central valve which is arranged coaxially and centrally within the rotor hub slidably.
- valve may be provided in the flow direction in front of one or more or even all ports and filters that protect the running surfaces between the piston and the central valve.
- camshaft alternating torques does not have to be provided for both directions of rotation. It is also possible to dispense with one of the two axially outermost switching positions 18 or 19. As a result, the camshaft alternating torques can then be used directly for faster adjustment only for the one direction of rotation.
- a use of the camshaft alternating torques can be provided for both directions of rotation, in which case, however, is dispensed with one of the two bypass check valves RSV-A, RSV-B.
- switch positions are possible. For example, it is possible to dispense with one or more positions or states or add one or more additional switch positions or states.
- On the hydraulic valve can also be provided a further switching position, wherein oil is metered through a self-centering center lock A and B, with one side is relieved to centering.
- the pin is relieved, allowing it to fall into the locking pin hole, locking the stage in the middle locking position.
- Center lock is used for example in the DE 10 2004 039 800 and DE 10 2009 022 869.1-13 shown.
- FIG. 2 shows a preferred piston 22 and is self-explanatory, especially in view of the above description.
- the webs 31, 32 are provided in the form of a shark fin shape, as in FIG FIG. 3 showing an enlarged view of the web 32.
- one or more tapered ridges may be provided on piston 22 or on bolt 27 or both.
- the web the webs only rejuvenated (rejuvenated) on one side or on both sides of the web.
- FIG. 4 There is preferably an opening of 1.5 mm at the point P to B1, preferably an opening of 1.5 mm at the location of B1 to B, preferably an overlap of 3.0 mm at the point B to T, preferably one Opening of 1.1 mm at the point P to A1, preferably an overlap of 1.6 mm at the point A1 to A and preferably an opening of 0.4 mm at the point A to T.
- FIG. 8 There is an opening of 0.0 mm at the point P to B1, preferably an overlap of 0.8 mm at the point B1 to B, preferably an overlap of 0.7 mm at the point B to T, preferably an opening of 0.4 mm at the point P to A1, preferably an opening of 0.4 mm at the point A1 to A and preferably an overlap of 1.9 mm at the point A to T.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Check Valves (AREA)
- Multiple-Way Valves (AREA)
Description
Die Erfindung betrifft einen Schwenkmotornockenwellenversteller mit einem Hydraulikventil, das zwei Arbeitsanschlüsse aufweist.The invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve having two working ports.
Die
Der
Eine Aufgabe einer Ausführungsform der vorliegenden Erfindung besteht in der Bereitstellung eines Schwenkmotornockenwellenverstellers, der auf Abstimmung durch elektronische Steuermittel gestattende einfache Weise gesteuert wird.It is an object of one embodiment of the present invention to provide a panning camshaft phaser that is controlled in a manner that is easily controlled by electronic control means.
Kurz gesagt stellt eine Ausführungsform der vorliegenden Erfindung einen Schwenkmotornockenwellenversteller bereit, der gewährleistet, dass durch Software Nockenwellenwechselmomente nur unter Bedingungen genutzt werden, unter denen das Drehmoment adäquat ist und/oder es wichtig ist, den Flussverbrauch zu reduzieren. Liegt ein zweistufiger Hub vor und ist das Nockenwellenwechselmoment bei niedrigem Hub nicht adäquat, kann die Software den Kolben zur Nutzung eines Teils des Nockenwellenwechselmoments positionieren, während zur schnelleren Verstellung Öl in den Tank geleitet wird.Briefly, an embodiment of the present invention provides a swing camshaft phaser that ensures that software can utilize camshaft cycle torques only under conditions where the torque is adequate and / or it is important to reduce flow consumption. If there is a two-stage stroke, and the low-lift camshaft alternating torque is not adequate, the software can position the piston to utilize part of the camshaft alternation torque while passing oil into the tank for faster adjustment.
Weitere Vorteile der Erfindung gehen aus der Beschreibung und den Zeichnungen hervor.Further advantages of the invention will become apparent from the description and the drawings.
Die vorliegende Erfindung wird im Folgenden in Verbindung mit den angehängten Zeichnungsfiguren beschrieben, in denen gleiche Bezugszahlen gleiche Elemente bezeichnen; es zeigen:
-
eine beispielhafte Ausführungsform eines Schaltschemas eines proportional ansteuerbaren Hydraulikventils, das in fünf Hauptstellungen betätigt werden kann;Figur 1 -
Figur 2 eine perspektivische Ansicht einer Kolbenkomponente des Hydraulikventils; -
eine vergrößerte Querschnittsansicht eines der Stege des Kolbens; undFigur 3 -
Figuren 4 - 10 eine beispielhafte konstruktive Umsetzung des Hydraulikventils nach in verschiedenen Stellungen.Figur 1
-
FIG. 1 an exemplary embodiment of a circuit diagram of a proportionally controllable hydraulic valve that can be operated in five major positions; -
FIG. 2 a perspective view of a piston component of the hydraulic valve; -
FIG. 3 an enlarged cross-sectional view of one of the webs of the piston; and -
FIGS. 4 to 10 an exemplary constructive implementation of the hydraulic valve afterFIG. 1 in different positions.
Die nachfolgende detaillierte Beschreibung stellt nur beispielhafte Ausführungsformen bereit und soll den Schutzumfang, die Anwendbarkeit oder die Konfiguration der Erfindung nicht einschränken. Stattdessen erhält der Fachmann durch die nachfolgende detaillierte Beschreibung der beispielhaften Ausführungsformen eine Beschreibung, die ihm die Umsetzung einer Ausführungsform der Erfindung ermöglicht. Es versteht sich, dass verschiedene Änderungen an Funktion und Anordnung von Elementen durchgeführt werden können, ohne von dem Gedanken und Schutzbereich der Erfindung, wie er in den angehängten Ansprüchen angeführt ist, abzuweichen.The following detailed description provides only exemplary embodiments and is not intended to limit the scope, applicability, or configuration of the invention. Instead, by the following detailed description of the exemplary embodiments, those skilled in the art will be given a description that enables them to practice an embodiment of the invention. It will be understood that various changes in the function and arrangement of elements may be made without departing from the spirit and scope of the invention as set forth in the appended claims.
Vom Hydraulikventil 3 gehen ein erster Arbeitsanschluss A und ein zweiter Arbeitsanschluss B zum Schwenkmotornockenwellenversteller 4 ab. Das Hydraulikventil 3 weist vier Anschlüsse und fünf Hauptschaltstellungen auf und kann somit auch als 4/5-Wege-Ventil mit einer Sperr-Mittelstellung 7 bezeichnet werden. Das Ventil hat im Prinzip sieben Zustände, aber die Schaltstellungen 7, 7a und 7b werden zum Halten der relativen Position des Rotors zum Stator verwendet, wobei die Schaltstellungen 7a und 7b Öl in die Anschlüsse B bzw. A lassen, wie zum Ausgleich von Systemleckage erforderlich ist. Obgleich sich die Ölführung in Schaltstellungen ändert, ist die Durchflussöffnung des Ventils durch inkrementale Positionierung in einem Schaltzustand variabel.From the
Um den Schwenkmotornockenwellenversteller 4 in die erste Drehrichtung 1 zu verschwenken, befindet sich das Hydraulikventil 3 in einer der beiden Schaltstellungen 16 oder 19, welche durch die beiden Kästchen rechts von der Sperr-Mittelstellung 7 dargestellt sind. In der Zeichnungsfigur 1 wird das Hydraulikventil 3 in Schaltstellung 19 bewegt, wenn das Hydraulikventil 3 durch den Aktuator die volle Hubbewegung erfährt. Dabei werden dieser Drehrichtung 1 zugeordnete Druckkammern 6 vom ersten Arbeitsanschluss A mit einem Druck beaufschlagt (der von dem Versorgungsanschluss P kommt).In order to pivot the
Hingegen werden in Schaltstellung 16 oder 19 dem zweiten Arbeitsanschluss B zugeordnete Druckkammern 5 entlastet. Der zweite Arbeitsanschluss B wird dazu in Schaltstellung 19 über einen Tankanschluss T auf einen Tank 20 geführt. In den Zwischenstellungen 7b und 16 zwischen der Sperr-Mittelstellung 7 bis zur Schaltstellung 19 werden die Druckkammern 6 von dem ersten Arbeitsanschluss A mit einem von dem Versorgungsanschluss P kommenden Druck beaufschlagt, aber der zweite Arbeitsanschluss B wird gegen den Tankanschluss T gesperrt.By contrast, in the
Umgekehrt gilt analoges. Das heißt, um den Schwenkmotornockenwellenversteller 4 in die zweite Drehrichtung 2 zu verschwenken, befindet sich das Hydraulikventil 3 in einer der beiden Schaltstellungen 18 oder 15, welche durch die beiden Kästchen links von der Sperr-Mittelstellung 7 dargestellt sind. In Zeichnungsfigur 1 ist das Hydraulikventil 3 durch die Feder 21 in Schaltstellung 18 in Kästchen vollständig ausgefahren. Auf diese Weise werden die dieser Drehrichtung 2 zugeordneten Druckkammern 5 von dem zweiten Arbeitsanschluss B mit Druck (mit einem Druck, der vom Versorgungsanschluss P kommt) beaufschlagt.Conversely, analogous applies. That is, to pivot the
In den Schaltstellungen 18 oder 15 werden hingegen dem ersten Arbeitsanschluss A zugeordnete Druckkammern 6 entlastet. In Schaltstellung 18 wird der erste Arbeitsanschluss A dazu über den Tankanschluss T auf den Tank 20 geführt. In den Zwischenstellungen 15 und 7a zwischen der Sperr-Mittelstellung 7 und bis Schaltstellung 18 werden die Druckkammern 5 von dem zweiten Arbeitsanschluss B mit einem Druck beaufschlagt, der vom Versorgungsanschluss P kommt, aber der erste Arbeitsanschluss A wird gegen den Tankanschluss T gesperrt.In the switching positions 18 or 15, however, the first working port A associated
In der Sperr-Mittelstellung 7 werden sämtliche vier Anschlüsse A, B, P, T gesperrt. Diese Schaltstellung sowie die Schaltstellungen 7a und 7b (die benachbarten Schaltstellungen) werden zum Halten des Rotors in einer konstanten Stellung relativ zum Stator verwendet.In the blocking middle position 7 all four ports A, B, P, T are blocked. This switch position as well as the switch positions 7a and 7b (the adjacent switch positions) are used to hold the rotor in a constant position relative to the stator.
Dazu liegt in der Schaltstellung 7a eine Verbindung des Versorgungsanschlusses P mit dem zweiten Arbeitsanschluss B vor, wohingegen der erste Arbeitsanschluss A gegen den Tankanschluss T gesperrt ist. In Schaltstellung 7a verhindert ein Zusammenwirken zwischen dem inneren Steg des Kolbens und dem Steg der Patrone oder des Zentralventilbolzens, dass der erste Arbeitsanschluss A gegenüber zu dem Versorgungsanschluss P geöffnet ist. Deshalb wird in Schaltstellung 7a verhindert, dass der erste Arbeitsanschluss A zu dem Tankanschluss T als auch zu dem Versorgungsanschluss P geöffnet ist.For this purpose, a connection of the supply connection P with the second working connection B is present in the
In Schaltstellung 7b liegt eine Verbindung des Versorgungsanschlusses P mit dem ersten Arbeitsanschluss A vor, während der zweite Arbeitsanschluss B gegen den Tankanschluss T gesperrt ist. In Schaltstellung 7b verhindert ein Zusammenwirken zwischen dem inneren Steg des Kolbens mit dem Steg der Patrone oder des Zentralventilbolzens, dass der zweite Arbeitsanschluss B zu dem Versorgungsanschluss P geöffnet ist. Deshalb wird in Schaltstellung 7b verhindert, dass der zweite Arbeitsanschluss B sowohl zu dem Tankanschluss T als auch dem Versorgungsanschluss P geöffnet ist. Die Schaltstellungen 7a und 7b bieten den Vorteil, dass der Versteller bei niedrigeren Pumpendrücken vollständig mit Öl gefüllt bleibt. Durch Sperren eines Arbeitsanschlusses gegen den Versorgungsanschluss P kann der Versorgungsanschluss P den anderen Arbeitsanschluss besser füllen.In switching
In den beiden äußersten Schaltstellungen 18 und 19 des Hydraulikventils 3 wird die Verstellung der Nockenwelle durch Belastung einer Seite der Flügel durch Nutzung von zurückgeführtem Öl, das infolge von Nockenwellenwechselmomenten zur Verfügung steht, in Verbindung mit vom Versorgungsanschluss P eingespeistem Öl bewerkstelligt. Druck wird von der anderen Seite der Flügel durch Zurückführen von Öl zu den belasteten Flügeln und gleichzeitig Leiten von Öl in den Tank entlastet. Dazu wird in der äußersten Schaltstellung 18 ein von einem dem ersten Arbeitsanschluss A zugeordneten Rückschlagventil RSV-A kommender Hydraulikfluid-Volumenstrom dem Versorgungsanschluss P und B zur Verfügung gestellt. Des Weiteren kann dazu in Schaltstellung 18 ein zusätzlicher A-Anschluss, der kein Rückschlagventil enthält, über den Tankanschluss T zum Tank 20 abführen. In Schaltstellung 19 hingegen wird ein von einem dem ersten Arbeitsanschluss A zugeordneten Rückschlagventil RSV-B kommender Hydraulikfluid-Volumenstrom dem Versorgungsanschluss P und A zur Verfügung gestellt. Des Weiteren kann dazu in Schaltstellung 19 ein zusätzlicher B-Anschluss, der kein Rückschlagventil enthält, über den Tankanschluss T zu Tank 20 abführen.In the two outermost switching positions 18 and 19 of the
Ebenso wird in Schaltstellungen 15 und 16 des Hydraulikventils 3 die Verstellung der Nockenwelle durch Belastung einer Seite der Flügel durch Nutzung von zurückgeführtem Öl, das infolge von Nockenwellenwechselmomenten zur Verfügung steht, in Verbindung mit vom Versorgungsanschluss P eingespeistem Öl bewerkstelligt. Anders als bei den Schaltstellungen 18 und 19 wird Druck von der anderen Seite der Flügel nur durch Zurückführen von Öl zu den belasteten Flügeln entlastet. Dazu wird in Schaltstellung 15 ein von einem dem ersten Arbeitsanschluss A zugeordneten Rückschlagventil RSV-A kommender Hydraulikfluid-Volumenstrom dem Versorgungsanschluss P und B zur Verfügung gestellt. In Schaltstellung 16 hingegen wird ein von einem dem zweiten Arbeitsanschluss B zugeordneten Rückschlagventil RSV-B kommender Hydraulikfluid-Volumenstrom dem Versorgungsanschluss P und A zur Verfügung gestellt. In Schaltstellungen 15 und 16 wird hingegen keine Verbindung irgendeines Anschlusses mit dem Tank 20 hergestellt.Also, in
In Schaltstellungen 15, 16, 18 und 19 wird dieser zusätzliche Volumenstrom vom zu entlastenden Arbeitsanschluss A oder B in den von einer Ölpumpe 12 kommenden Volumenstrom am Versorgungsanschluss P eingespeist. Es liegt eine Verbindung vom Versorgungsanschluss P über ein Pumpenrückschlagventil RSV-P zur Ölpumpe 12 vor, die den Druck zur Verstellungsunterstützung des Schwenkmotornockenwellenverstellers 4 aufbringt. Dieses Pumpenrückschlagventil RSV-P sperrt dabei die Drücke im Hydraulikventil 3 ein, so dass von dem zu entlastenden Arbeitsanschluss A bzw. B kommende Spitzendrücke zu einem größeren Anteil der Verstellungsunterstützung zur Verfügung gestellt werden können, als dies bei einer offenen Ölpumpenleitung 14a, 14b der Fall wäre.In switching
Axial zwischen den beiden Außenstegen 23, 24 sind zwei schmale Rippen oder Stege 31, 32 vorgesehen, die um den Kolben 22 herumlaufen. Diese umlaufenden Rippen 31, 32 entsprechen zwei sich von dem Zentralbolzen 27 radial nach innen erstreckenden Ringstegen 33, 34. Zusätzlich zu diesen beiden Ringstegen 33, 34 sind noch zwei axial äußere Ringstege 35, 36 vorgesehen. Diese vier Ringstege 33, 34, 35, 36 werden dadurch gebildet, dass fünf Innenringnuten 37, 38, 39, 40, 41 aus dem Zentralbolzen 27 ausgehöhlt sind. In diese fünf Innenringnuten 37, 38, 39, 40, 41 münden fünf Anschlussbohrungen 60, 62, 64, 66, 68, die durch die Wand des Zentralbolzens 27 gebohrt sind. In Abhängigkeit von den Strömungsanforderungen sind mehr als eine Bohrung pro Ringnut möglich.Axially between the two
Diese fünf Anschlussbohrungen 60, 62, 64, 66, 68 bilden von Seiten des Elektromagneten 17 axial entlang des Bolzens 27 Folgendes: eine dem zweiten Arbeitsanschluss B zugehörige Standardöffnung B, eine dem zweiten Arbeitsanschluss B zugehörige Öffnung B1 zur Nutzung von Nockenwellenwechselmomenten, den Versorgungsanschluss P, eine dem ersten Arbeitsanschluss A zugehörige Öffnung A1 und eine dem ersten Arbeitsanschluss A zugehörige Öffnung A zur Nutzung von Nockenwellenwechselmomenten.These five connection bores 60, 62, 64, 66, 68 form from the sides of the
An den beiden Arbeitsanschlüssen A, B sind somit jeweils zwei Öffnungen A, A1 bzw. B, B1 vorgesehen. Von diesen sind die axial inneren Öffnungen A1, B1 für eine Nockenwellenwechselmomentennutzung vorgesehen. Im Gegensatz zu den ausschließlich mit den Außenstegen 23, 24 von innen sperrbaren axial äußeren Öffnungen A, B weisen die axial inneren Öffnungen A1, B1 die bandförmigen Rückschlagventile RSV-A, RSV-B auf. Jeweils eines der bandförmigen Rückschlagventile RSV-A bzw. RSV-B ist in eine Innenringnut 40 bzw. 38 radial innerhalb der axial inneren Öffnungen A1 bzw. B1 des Zentralbolzens 27 eingesetzt. Mit den Rückschlagventilen RSV-A, RSV-B ist es gemäß dem in der
Zudem ist noch das bandförmige Pumpenrückschlagventil RSV-P in einer Innenringnut 39 vorgesehen. Dieses Pumpenrückschlagventil RSV-P ist grundsätzlich gleich aufgebaut, wie die beiden Rückschlagventile RSV-A, RSV-B. Jedoch kann dieses Pumpenrückschlagventil RSV-P eine andere Ansprechkraft aufweisen.In addition, the band-shaped pump check valve RSV-P is still provided in an
In der Schaltstellung 18 gemäß
Damit kann in dieser Schaltstellung 18 Hydraulikfluid vom Versorgungsanschluss P über das Pumpenrückschlagventil RSV-P zu der dem zweiten Arbeitsanschluss B zugehörigen Standardöffnung B gelangen. Die beiden anderen Rückschlagventile RSV-A und RSV-B sperren dabei die Öffnungen A1 und B1 gegen Drücke vom Versorgungsanschluss P und aus der dem zweiten Arbeitsanschluss B zugehörigen Standardöffnung B. Hingegen werden kurzfristige Spitzendrücke infolge der Nockenwellenwechselmomente aus der dem ersten Arbeitsanschluss A zugehörigen Öffnung A1 durch dessen Rückschlagventil RSV-A durchgelassen. Wenn der den Arbeitsanschluss A betreffende Druck aufgrund von einem Nockenmoment hoch ist, ist er größer als der Druck P. Dann öffnet sich das RSV-A-Rückschlagventil und leitet Öl von A, während sich das P-Rückschlagventil (RSV-P) schließt. In Schaltstellung 18 wird Druck vom ersten Arbeitsanschluss A von A zu B (über Öffnung A1) zurückgeführt, der erste Arbeitsanschluss A wird auch (über Standardöffnung A und Strömungsfläche 30) zum Tankanschluss T entlastet.Thus, in this
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Einer der Hauptvorteile des hierin beschriebenen Systems besteht darin, dass durch Softwaresteuerung des Hydraulikventils die Einschaltdauer (oder der Strom) darauf beschränkt werden kann, nur dann Rückführung zu gestatten (Schaltstellungen 15 und 16), wenn ein adäquates Nockenmoment vorliegt, um gewünschte Phasenraten zu erreichen. Es kann auch auf die Schaltstellungen 15 und 16 beschränkt werden, wenn ungenügender Strom im Motorölsystem vorhanden ist und weitere Belastung nicht wünschenswert ist.One of the major advantages of the system described herein is that by software control of the hydraulic valve, the duty cycle (or current) may be limited to allowing feedback only (switch
Wenn ein Nockenmoment nicht adäquat ist, wie zum Beispiel im Niedrighubmodus eines zweistufigen Hubsystems, gestattet die Software die Nutzung der Schaltstellungen 18 und 19 zur Phasenverstellung. Hohe Umdrehungen pro Minute gestatten auch nicht genügend Zeit, Nockenmomentimpulse gut auszunutzen, somit kann die Nutzung der Schaltstellungen 18 und 19 Phasenverstellungsgeschwindigkeiten bei hohen Umdrehungen pro Minute erhöhen, falls erforderlich. Das Ausmaß der Strömungsöffnung zum Tankanschluss T und die Ventilhubstellungen, in denen die Schaltstellungen 18 und 19 beginnen, können speziell auf die Anwendung zugeschnitten sein.If a cam torque is not adequate, such as in the low lift mode of a two-stage lift system, the software allows the use of the shift positions 18 and 19 for phasing. High revolutions per minute also do not allow enough time to make good use of cam torque pulses, thus utilizing
Bei der dargelegten beispielhaften Ausführungsform werden die Standardöffnung A oder B und die Öffnung A1 oder B1 kombiniert, um Nockenwellenwechselmomente zunächst außerhalb des Zentralbolzens 27 zum Arbeitsanschluss A bzw. B zu nutzen. Bei einer alternativen Ausführungsform ist es auch möglich, die Standardöffnung A oder B und die Öffnung A1 oder B1 auch innerhalb des Zentralbolzens 27 zu kombinieren, um die Nockenwellenwechselmomente zu nutzen.In the exemplary embodiment set forth, the standard opening A or B and the opening A1 or B1 are combined to initially utilize camshaft alternating moments outside of the
Bei einer anderen alternativen Ausführungsform können anstelle von Bandrückschlagventilen auch Kugelrückschlagventile verwendet werden. So ist es beispielsweise auch möglich, innerhalb des Hydraulikventils Kugelrückschlagventile zu verwenden, wie dies beispielsweise die
Je nach Einsatzbedingungen des Ventils können in Flussrichtung vor einem oder mehreren bzw. sogar allen Anschlüssen auch Filter vorgesehen sein, welche die Laufflächen zwischen dem Kolben und dem Zentralventil schützen.Depending on the operating conditions of the valve may be provided in the flow direction in front of one or more or even all ports and filters that protect the running surfaces between the piston and the central valve.
Die Nutzung von Nockenwellenwechselmomenten muss nicht für beide Drehrichtungen vorgesehen sein. Es ist auch möglich, auf eine der beiden axial äußersten Schaltstellungen 18 oder 19 zu verzichten. Demzufolge sind dann nur für die eine Drehrichtung die Nockenwellenwechselmomente direkt zur schnelleren Verstellung nutzbar.The use of camshaft alternating torques does not have to be provided for both directions of rotation. It is also possible to dispense with one of the two axially outermost switching positions 18 or 19. As a result, the camshaft alternating torques can then be used directly for faster adjustment only for the one direction of rotation.
Bei einer alternativen Ausführungsform kann auch für beide Drehrichtungen eine Nutzung der Nockenwellenwechselmomente vorgesehen sein, wobei dann jedoch auf eines der beiden Umgehungs-Rückschlagventile RSV-A, RSV-B verzichtet wird.In an alternative embodiment, a use of the camshaft alternating torques can be provided for both directions of rotation, in which case, however, is dispensed with one of the two bypass check valves RSV-A, RSV-B.
Dabei sind beliebige Kombinationen von Schaltstellungen möglich. So ist es zum Beispiel möglich, auf eine oder mehrere Stellungen oder Zustände zu verzichten oder eine oder mehrere zusätzliche Schaltstellungen oder Zustände hinzuzufügen.Any combinations of switch positions are possible. For example, it is possible to dispense with one or more positions or states or add one or more additional switch positions or states.
Am Hydraulikventil kann auch noch eine weitere Schaltstellung vorgesehen sein, wobei durch eine selbstzentrierende Mittenverriegelung A und B Öl zudosiert wird, wobei eine Seite bis zur Zentrierung entlastet wird. Der Stift wird entlastet, wodurch er in das Verriegelungsstiftloch fallen kann, wodurch der Versteller in der mittleren Verriegelungsstellung verriegelt wird. Mittenverriegelung wird beispielsweise in der
Es sollte aufgezeigt werden, dass am Kolben 22 oder am Bolzen 27 oder an beiden ein oder mehrere sich verjüngende(r) Steg(e) (wie zum Beispiel in Haifischflossenform) vorgesehen sein können. Darüber hinaus ist es möglich, dass sich der Steg (die Stege) nur auf einer Seite oder auf beiden Seiten des Stegs verjüngt (verjüngen).It should be pointed out that one or more tapered ridges (such as in shark fin shape) may be provided on
Andere Vorzüge der Bereitstellung dünner Stege bestehen darin, dass dadurch kürzere Kolbenhübe gestattet werden. Darüber hinaus wird dadurch ein besseres Zeitverhalten für die proportionale Regelung des Ventils gestattet. Dies ist darauf zurückzuführen, dass dadurch der den Schaltstellungen 7a bis 7b zugeordnete Hub verkürzt werden kann, wodurch ein schnellerer Übergang von einer Richtung zur anderen gestattet wird.Other advantages of providing thin webs are that it allows shorter piston strokes. In addition, this allows a better timing for the proportional control of the valve. This is due to the fact that thereby the stroke associated with the switch positions 7a to 7b can be shortened, allowing a faster transition from one direction to another.
Unter Bezugnahme auf die
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Bei den beschriebenen Ausführungsformen handelt es sich nur um beispielhafte Ausführungsformen. Eine Kombination der beschriebenen Merkmale für unterschiedliche Ausführungsformen ist ebenfalls möglich. Weitere, insbesondere nicht beschriebene Merkmale der zur Erfindung gehörenden Vorrichtungsteile, sind den in den Zeichnungen dargestellten Geometrien der Vorrichtungsteile zu entnehmen.The described embodiments are only exemplary embodiments. A combination of the described features for different embodiments is also possible. Further, in particular not described features of the device parts belonging to the invention are to be taken from the geometries of the device parts shown in the drawings.
Zum Beispiel können die Rückschlagventile als Kugel- oder Platten-Rückschlagventile ausgestaltet sein.For example, the check valves may be configured as ball or plate check valves.
Claims (13)
- Pivoting-motor camshaft adjuster (4) having a hydraulic valve (3) which comprises two working connectors (A, B), a supply connector (P) and a tank connector (T), the hydraulic valve (3) being configured to prevent that one of the working connectors (A, B) is relieved to the tank connector (T) while the supply connector (P) of the other working connector (B, A) is loaded with pressure, the two working connectors (A, B) comprising a first working connector (A) and a second working connector (B), the hydraulic valve (3) being configured at least to provide the following:a first state, during which the supply connector (P) loads the first working connector (A) with pressure, while the second working connector (B) permits a return into the first working connector (A) and at the same time is relieved to the tank connector (T), characterized in that the hydraulic valve (3) is also configured to provide the following states:a second state, during which the supply connector (P) loads the first working connector (A) with pressure, while the second working connector (B) returns to the first working connector (A), but is not relieved to the tank connector (T); anda third state, during which the supply connector (P) loads the first working connector (A) with pressure, while it is prevented that the second working connector (B) returns to the first working connector (A), and it is prevented that it is relieved to the tank connector (T).
- Pivoting-motor camshaft adjuster (4) according to Claim 1, each working connector (A, B) having a standard opening (A, B) and an additional opening (A1, B1) for utilizing pressure peaks as a consequence of camshaft alternating torques.
- Pivoting-motor camshaft adjuster (4) according to Claim 1 or 2, each standard opening (A, B) being configured for targeted relief to the tank connector (T).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 3, the hydraulic valve (3) being configured to permit a return from the one working connector (A, B) to the other working connector (B, A), while it prevents that the one working connector (A, B) is relieved to the tank connector (T), and while the supply connector (P) loads the other working connector (B, A) with pressure.
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 3, the hydraulic valve (3) being configured to prevent a return from the one working connector (A, B) to the other working connector (B, A), while it prevents that one working connector (A, B) is relieved to the tank connector (T), and while the supply connector (P) loads the other working connector with pressure.
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 5, the hydraulic valve (3) comprising a piston (22) and/or a pin (27) with at least one tapering web (31, 32).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 6, the hydraulic valve (3) comprising a piston (22) and/or a pin (27) with at least one web (31, 32) with a shark fin shape on at least one side (90) of the web (31, 32).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding claims, each working connector (A, B) having a standard opening (A, B) and an additional opening (A1, B1) for utilizing the pressure peaks as a consequence of camshaft alternating torques, and check valves (RSV-A, RSV-B) being provided at the additional opening (A1, B1) of each working connector (A, B).
- Pivoting-motor camshaft adjuster (4) according to Claim 8, a check valve (RSV-P) being provided at the supply connector (P).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 3 to 9, the hydraulic valve (3) being configured, in the case of a movement of the hydraulic valve (3) from one position to another position, to increasingly permit a throughflow from the supply connector (P) to the one working connector (A, B) and to increasingly permit a return from the other working connector (B, A) into the one working connector (A, B).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 3 to 10, the hydraulic valve being configured, in the case of a movement of the hydraulic valve (3) from a first position to a second position, to increasingly permit a throughflow from the supply connector (P) to the one working connector (A, B) and to increasingly permit a return from the other working connector (B, A) into the one working connector (A, B) if the pressure of the one working connector (A, B) increases as a result of cam torque pulses above the pressure of the second working connector (B, A) and of the supply connector (P).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 11, the hydraulic valve (3) being configured, in the case of a movement of the hydraulic valve (3) from one position to another position, to increasingly permit a throughflow from the one working connector (A, B) to the tank connector (T) and to increasingly permit a return of the one working connector (A, B) to the other working connector (B, A).
- Pivoting-motor camshaft adjuster (4) according to one of the preceding Claims 1 to 12, the hydraulic valve (3) being configured to provide seven states:the first state, during which the supply connector (P) loads the first working connector (A) with pressure, while the second working connector (B) permits a return into the first working connector (A) and at the same time is relieved to the tank connector (T);the second state, during which the supply connector (P) loads the first working connector (A) with pressure, while the second working connector (B) returns to the first working connector (A) but is not relieved to the tank connector (T);the third state, during which the supply connector (P) loads the first working connector (A) with pressure, while it is prevented that the second working connector (B) returns to the first working connector (A), and it is prevented that it is relieved to the tank connector (T);a fourth state, during which it is prevented that neither the first nor the second working connector (A, B) are loaded with pressure by way of the supply connector (P), and it is prevented that they are relieved to the tank connector (T);a fifth state, during which the supply connector (P) loads the second working connector (B) with pressure, while it is prevented that the first working connector (A) returns to the second working connector (B), and it is prevented that it is relieved to the tank connector (T);a sixth state, during which the supply connector (P) loads the second working connector (B) with pressure, while the first working connector (A) returns to the second working connector (B), but is not relieved to the tank connector (T); anda seventh state, during which the supply connector (P) loads the second working connector (B) with pressure, while the first working connector (A) permits a return into the first working connector (A) and at the same time is relieved to the tank connector (T).
Applications Claiming Priority (1)
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US14/174,594 US9341090B2 (en) | 2014-02-06 | 2014-02-06 | Oscillating-motor camshaft adjuster having a hydraulic valve |
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EP2905434A1 EP2905434A1 (en) | 2015-08-12 |
EP2905434B1 true EP2905434B1 (en) | 2017-09-27 |
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US (1) | US9341090B2 (en) |
EP (1) | EP2905434B1 (en) |
JP (1) | JP6218129B2 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018135586A1 (en) * | 2017-01-19 | 2018-07-26 | 株式会社デンソー | Valve timing adjustment device |
DE102018126302A1 (en) * | 2018-01-30 | 2019-08-01 | ECO Holding 1 GmbH | Swivel motor adjuster for a camshaft and camshaft arrangement with a camshaft and a Schwenkmotorversteller |
EP3530891B1 (en) * | 2018-02-21 | 2021-03-03 | ECO Holding 1 GmbH | Hydraulic valve for a pivoting engine adjuster of a camshaft |
DE102019101115A1 (en) | 2018-02-21 | 2019-08-22 | ECO Holding 1 GmbH | Hydraulic valve for a Schwenkmotorversteller a camshaft |
EP3530892B1 (en) * | 2018-02-21 | 2021-05-19 | ECO Holding 1 GmbH | Hydraulic valve for a pivoting engine adjuster of a camshaft |
FR3083569B1 (en) * | 2018-07-04 | 2020-11-27 | Delphi Automotive Systems Lux | CAMSHAFT DEPHASER CONTROL DEVICE |
US11174760B2 (en) * | 2018-12-11 | 2021-11-16 | Delphi Technologies Ip Limited | Camshaft phaser |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2375014A1 (en) * | 2010-04-10 | 2011-10-12 | Hydraulik-Ring GmbH | Camshaft phaser comprising a hydraulic valve |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3873525B2 (en) * | 1999-05-31 | 2007-01-24 | 株式会社デンソー | Valve timing adjustment device |
US6766777B2 (en) | 2002-06-14 | 2004-07-27 | Borgwarner, Inc. | Method to ensure robust operation of a pin lock in a vane style cam phaser |
DE102004039800B4 (en) | 2004-08-17 | 2006-07-27 | Hydraulik-Ring Gmbh | Cam Phaser System |
DE102006012775B4 (en) | 2006-03-17 | 2008-01-31 | Hydraulik-Ring Gmbh | Fast cam phaser hydraulic circuit, in particular for camshaft adjuster, and corresponding control |
EP1996819B1 (en) * | 2006-03-17 | 2012-04-11 | Hilite Germany GmbH | Hydraulic circuit, especially for camshaft adjusters, and corresponding control element |
DE102006012733B4 (en) | 2006-03-17 | 2008-03-27 | Hydraulik-Ring Gmbh | Fast cam phaser hydraulic circuit, in particular for camshaft adjuster, and corresponding control |
WO2007107426A1 (en) * | 2006-03-17 | 2007-09-27 | Hydraulik-Ring Gmbh | Hydraulic circuit, in particular for camshaft adjuster, and corresponding control element |
WO2008067935A2 (en) | 2006-12-04 | 2008-06-12 | Daimler Ag | Regulating device |
DE102007007072A1 (en) | 2007-02-13 | 2008-08-14 | Schaeffler Kg | Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine |
DE102007012967B4 (en) | 2007-03-14 | 2009-01-08 | Hydraulik-Ring Gmbh | Valve, in particular cartridge valve, with integrated non-return valve |
JP4518149B2 (en) | 2008-01-10 | 2010-08-04 | 株式会社デンソー | Valve timing adjustment device |
DE102008036877B4 (en) | 2008-08-07 | 2019-08-22 | Schaeffler Technologies AG & Co. KG | Camshaft adjusting device for an internal combustion engine |
DE102009022869A1 (en) | 2009-05-27 | 2010-12-09 | Hydraulik-Ring Gmbh | Vane phaser system |
DE102009030201A1 (en) * | 2009-06-24 | 2010-12-30 | Schaeffler Technologies Gmbh & Co. Kg | Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine |
JP2011196245A (en) * | 2010-03-19 | 2011-10-06 | Denso Corp | Valve timing adjusting device |
DE102010013777A1 (en) | 2010-04-03 | 2011-10-06 | Hydraulik-Ring Gmbh | Central valve for oscillating motor adjuster, has hollow piston that is guided within connector which has radial oil supply connection and two radial working connections |
DE102010022896B4 (en) | 2010-06-07 | 2021-11-11 | Schaeffler Technologies AG & Co. KG | Camshaft adjusting device for an internal combustion engine that can be actuated by pressure medium |
-
2014
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2015
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- 2015-02-04 JP JP2015020768A patent/JP6218129B2/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2375014A1 (en) * | 2010-04-10 | 2011-10-12 | Hydraulik-Ring GmbH | Camshaft phaser comprising a hydraulic valve |
Also Published As
Publication number | Publication date |
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CN104832239B (en) | 2017-12-15 |
KR101614777B1 (en) | 2016-06-03 |
JP2015148229A (en) | 2015-08-20 |
KR20150099407A (en) | 2015-08-31 |
US20150218976A1 (en) | 2015-08-06 |
US9341090B2 (en) | 2016-05-17 |
CN104832239A (en) | 2015-08-12 |
JP6218129B2 (en) | 2017-10-25 |
EP2905434A1 (en) | 2015-08-12 |
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