EP2375014A1 - Camshaft phaser comprising a hydraulic valve - Google Patents
Camshaft phaser comprising a hydraulic valve Download PDFInfo
- Publication number
- EP2375014A1 EP2375014A1 EP11157216A EP11157216A EP2375014A1 EP 2375014 A1 EP2375014 A1 EP 2375014A1 EP 11157216 A EP11157216 A EP 11157216A EP 11157216 A EP11157216 A EP 11157216A EP 2375014 A1 EP2375014 A1 EP 2375014A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic valve
- port
- opening
- hydraulic
- switching position
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 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 claims 3
- 239000012530 fluid Substances 0.000 claims description 12
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 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
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 239000000446 fuel Substances 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
-
- 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 according to the preamble of claim 1.
- the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already relate to a Schwenkmotornockenwellenversteller with a hydraulic valve, which has 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 4/3-way valve in cartridge design.
- In the sleeve check valves are used on the inside, which are designed as band-shaped rings. By means of these check valves camshaft alternating torques are used to adjust the camshaft adjuster particularly fast or with a relatively low oil pressure can.
- the check valves cover the openings for the use of pressure peaks due to camshaft alternating torques.
- the object of the invention is to provide a simple to be controlled with little effort Schwenkmotornockenwellenversteller.
- the camshaft alternating torques for fast phasing of the camshaft can be used in the invention Schwenkmotornockenwellenversteller. Moreover, due to the use of camshaft alternating torques, it is advantageously possible to enable adjustment with a relatively low oil pressure. A thus possible small dimensions of the oil pump improves the efficiency of the internal combustion engine. The saved volume flow of hydraulic fluid is different Consumers, such as a hydraulic valve lift adjustment available.
- Pivot camshaft phasors have also recently been applied to the combustion engines with fewer cylinders to reduce fuel consumption, increase performance, and reduce exhaust emissions.
- the smaller the number of cylinders the greater the fluctuations of the Nockwellen dockmomente.
- the hydraulic valve is proportional to a first switching position adjustable in which the effect of check valves for the use of camshaft alternating torques is bypassed. Due to the proportional controllability of the control process between use of the camshaft alternating torques and circumvention of this use is continuously controlled.
- the hydraulic valve is additionally adjustable in favor of a higher control quality in a switching position to bypass the use of camshaft alternating torque.
- Fig. 1 shows in a circuit diagram a by means of an electromagnet 17 against a spring force of a spring 21 operable hydraulic valve 3, which is controlled proportionally.
- a Schwenkmotornockenwellenversteller 4 is pivotable.
- the angular position between the crankshaft and the camshaft is changed during operation of an internal combustion engine.
- the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine brings its optimal performance at the respective speed.
- the Schwenkmotornockenwellenversteller 4 allows a continuous adjustment of the camshaft relative to the crankshaft.
- a first consumer port A and a second consumer port B go to the Schwenkmotornockenwellenversteller 4 from.
- the hydraulic valve 3 has four ports and five shift positions and can thus also be referred to as a 4/5-way valve with a locking middle position 7.
- the hydraulic valve 3 is in one of the two switching positions 16, 19, which are represented by the two switch box behind the locking center position 7.
- the hydraulic valve is in the switch position 19 of the switch box at the very rear.
- pressure chambers 6 associated with this direction of rotation 1 are acted upon by the first consumer port A, which pressure comes from a supply port P.
- the pressure chambers 5 assigned to the second, ie opposite, direction of rotation 2 are relieved to the second consumer connection B.
- the second consumer port B is guided to a tank 20 via a tank connection T.
- the adjustment of the camshaft takes place with use of the camshaft alternating torques.
- an outermost switching position 18 similar to the immediately adjacent switching position 15 is executed.
- a volume flow from the hydraulic fluid coming from a check valve RSV-A assigned to the first supply connection A is made available to the supply connection P.
- the other outermost switching position 19 is similar to the immediately adjacent switching position 16 executed.
- a volume flow of hydraulic fluid coming from a check valve RSV-B assigned to the second supply connection B is made available to the supply connection P.
- This additional volume flow from the load connection A or B to be relieved is fed into the volume flow coming from an oil pump 12 at the supply connection P.
- the supply port P leads via a pump check valve RSV-P to the oil pump 12, which applies the pressure for adjusting the Schwenkmotornockenwellenverstellers 4.
- This pump check valve RSV-P blocks the pressures in the hydraulic valve 3 so that peak pressures coming from the load connection A or B to be relieved can be made available to a larger proportion of the adjustment assistance than is the case with an open oil pump line 14a, 14b would.
- Fig. 2 to Fig. 6 show a constructive embodiment of the hydraulic valve 3 in the five switching positions 18, 15, 7, 16, 19 according to Fig. 1 ,
- Fig. 2 shows the hydraulic valve 3 in the first switching position 18, in which the electromagnet 17 according to Fig. 1 a hollow piston 22 of the hydraulic valve 3 does not move.
- the stroke of the piston 22 is thus at zero.
- the piston 22 is displaceable within a bushing 27 against the force of the spring designed as a helical compression spring 21.
- the electromagnet 17 facing the front end is closed to produce a contact surface for an actuating plunger of the electromagnet 17, whereas the other end face for the realization of the tank port T is open.
- the piston 22 has at its two ends outer webs 23, 24, which are guided relative to the bushing 27.
- the two outer webs 23, 24 are pierced by transverse bores 29, 30, so that from these transverse bores 29, 30 via the interior of the hollow piston 22 access to the tank port T is present.
- two narrow ribs 31, 32 are provided, which rotate around the piston 22.
- These circumferential ribs 31, 32 correspond to two annular webs 33, 34 extending radially inwardly from the bush 27.
- two axially outer annular webs 35, 36 are provided.
- These four ring lands 33 to 26 are formed, since five inner ring grooves 37 to 41 are turned out of the socket. In this five réelleringnuten 37 to 41 five connection holes, which are drilled through the wall of the socket 27 open.
- the axially inner openings A2, B2 for provided a camshaft alternating torque use.
- the axially inner openings A2, B2 have the band-shaped check valves RSV-A, RSB-B.
- one of the band-shaped check valves RSV-A and RSB-B is inserted into an inner annular groove 25 and 26 radially inside the axially inner openings A2 and B2 of the bush 27.
- band-shaped pump check valve RSV-P is still provided in an inner annular groove 28.
- This 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 other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the the second working port B associated standard opening B1.
- short-term peak pressures due to the camshaft alternating torques from the first working port A associated opening A2 through its check valve RSV-A.
- the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
- the hydraulic valve 3 is in the switching position 15.
- the rear rib 32 covers the corresponding annular land 34 so far that a flow through the very narrow gap is possible only with increased flow resistance.
- the very slightly biased check valve RSV-A has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the first working port A to the second working port B.
- the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
- the hydraulic valve 3 is in the locking center position 7.
- the supply port P is closed by the two ribs 31, 32.
- the ribs 31, 31 cover the corresponding annular webs 33, 34 in a correspondingly large extent.
- the two working connections A, B are blocked against the tank drain T.
- both transverse bores 29, 30 are located axially outside the axially outer inner annular grooves 37, 41.
- the hydraulic valve 3 is in the switching position 16.
- coming from the supply port P hydraulic fluid through the gap between the rear rib 32 and the corresponding ring land 34 to the standard opening A1 of the first working port A pass.
- the front rib 31 covers the corresponding annular web 33 so far that a flow through the very narrow Gap is only possible with increased flow resistance.
- the very slightly biased check valve RSV-B has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the second working port B to the first working port A.
- the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
- 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 and the standard opening B1 of the second working port B for this purpose.
- the outer web 23 and the foremost annular web 35 overlap over a large sealing length. In this way, in this switching position 19 hydraulic fluid can reach from the supply connection P via the pump check valve RSV-P to the standard opening A1 of the first working connection A.
- the other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the standard opening B1 of the second working port B.
- short-term peak pressures due to the camshaft alternating torques from the opening B2 of the second working port B by the Check valve RSV-B let through.
- the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
- the standard opening A1 or B1 and the opening A2 or B2 are summarized for use of camshaft alternating moments only outside the bushing 27 to the working port A and B respectively.
- an annular groove can be incorporated radially outside into the socket.
- ball check valves may be used instead of band check valves.
- the ball check valves need not necessarily be installed in the socket of a cartridge valve. It is also possible, for example, to use the ball check valves in a rotor and run the piston as a central valve which is arranged coaxially and centrally within the rotor hub slidably.
- screens may also be provided in the direction of flow in front of one or more or even all ports, which protect the running surfaces between the piston and the bushing.
- the hydraulic valve can also find application in a so-called central valve.
- the socket is not directly connected to the magnetic part. Instead, the hydraulic valve is centrally located in the rotor of the Schwenkmotornockenwellenverstellers so that the sleeve rotates together with the piston.
- the magnet is rotationally fixed relative to the cylinder head arranged, so that a relative movement between the plunger of the magnetic member and the piston takes place.
- 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 position 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, but then to one of the two check valves RSV-A, RSV-B bypassing switch positions 15, 16 is omitted.
- a further switching position in which both working ports A, B are relieved against the tank port T, so that a so-called center locking is made possible.
- a locking bolt is provided in the Schwenkmotornockenwellenversteller, which fixes the rotor in an angular position against the stator, which is not an end position.
- Such a central locking is for example in the DE 10 2004 039 800 B4 and the not pre-published DE 10 2009 022 869.1-13 shown.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Die Erfindung betrifft ein Schwenkmotornockenwellenversteller mit einem Hydraulikventil nach dem Oberbegriff von Patentanspruch 1.The invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve according to the preamble of claim 1.
Die
Aufgabe der Erfindung ist es, einen mit geringem Abstimmungsaufwand einfach zu regelnden Schwenkmotornockenwellenversteller zu schaffen.The object of the invention is to provide a simple to be controlled with little effort Schwenkmotornockenwellenversteller.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen von Patentanspruch 1 gelöst.This object is achieved with the features of claim 1.
Gemäß einem Vorteil der Erfindung sind beim erfindungsgemäßen Schwenkmotornockenwellenversteller die Nockenwellenwechselmomente zur schnellen Phasenverstellung der Nockenwelle nutzbar. Überdies ist es infolge der Nutzung von Nockenwellenwechselmomenten in vorteilhafter Weise möglich, eine Verstellung mit einem relativ geringen Öldruck zu ermöglichen. Eine damit mögliche geringe Dimensionierung der Ölpumpe verbessert den Wirkungsgrad des Verbrennungsmotors. Der eingesparte Volumenstrom an Hydraulikfluid steht anderen Verbrauchern, wie beispielsweise einer hydraulischen Ventilhubverstellung zur Verfügung.According to one advantage of the invention, the camshaft alternating torques for fast phasing of the camshaft can be used in the invention Schwenkmotornockenwellenversteller. Moreover, due to the use of camshaft alternating torques, it is advantageously possible to enable adjustment with a relatively low oil pressure. A thus possible small dimensions of the oil pump improves the efficiency of the internal combustion engine. The saved volume flow of hydraulic fluid is different Consumers, such as a hydraulic valve lift adjustment available.
In jüngster Vergangenheit finden Schwenkmotornockenwellenversteller zwecks Kraftstoffverbrauchssenkung, Leistungssteigerung und Schadstoffausstoßverringerung auch bei den Vebrennungsmotoren mit weniger Zylindern Anwendung. Je geringer die Anzahl der Zylinder, desto größer sind die Schwankungen der Nockwellenwechselmomente. Mit der Nutzung der sehr stark schwankenden Nockenwellenwechselmomente zur Phasenverstellung geht jedoch ein hoher Abstimmungsbedarf der Regelung des Hydraulikventils einher. Gemäß einem weiteren Vorteil der Erfindung ist das Hydraulikventil proportional in eine erste Schaltstellung regelbar, in der die Wirkung von Rückschlagventilen zur Nutzung von Nockenwellenwechselmomenten umgangen wird. Infolge der proportionalen Regelbarkeit ist der Regelvorgang zwischen Nutzung der Nockenwellenwechselmomente und Umgehung dieser Nutzung stufenlos steuerbar. Somit ist das Hydraulikventil zugunsten einer höheren Regelgüte zusätzlich in eine Schaltstellung zur Umgehung der Nockenwellenwechselmomentennutzung regelbar.Pivot camshaft phasors have also recently been applied to the combustion engines with fewer cylinders to reduce fuel consumption, increase performance, and reduce exhaust emissions. The smaller the number of cylinders, the greater the fluctuations of the Nockwellenwechselmomente. With the use of the highly fluctuating camshaft alternating torques for phase adjustment, however, there is a high need for coordination of the control of the hydraulic valve. According to a further advantage of the invention, the hydraulic valve is proportional to a first switching position adjustable in which the effect of check valves for the use of camshaft alternating torques is bypassed. Due to the proportional controllability of the control process between use of the camshaft alternating torques and circumvention of this use is continuously controlled. Thus, the hydraulic valve is additionally adjustable in favor of a higher control quality in a switching position to bypass the use of camshaft alternating torque.
In den Unteransprüchen wird eine konstruktiv besonders einfache Umsetzung eines solchen Hydraulikventils beansprucht. Gegenüber dem in der
In besonders vorteilhafter Weise ist es damit möglich, ein solches erfindungsgemäßes Hydraulikventil mit vielen Gleichteilen zu fertigen, welche von Hydraulikventilen ohne Umgehung der Nockenwellenwechselmomentennutzung oder sogar gänzlich ohne Nockenwellenwechselmomentennutzung stammen. Ebenso besteht ein hohes Gleichteilepotential mit Hydraulikventilen mit Mittenverriegelung. Eine solche Gleichteilestrategie unter Veränderung des Kolbens ist beispielsweise in der nicht vorveröffentlichten
Weitere Vorteile der Erfindung gehen aus den weiteren Patentansprüchen, der Beschreibung und der Zeichnung hervor.Further advantages of the invention will become apparent from the other claims, the description and the drawings.
Die Erfindung ist nachfolgend anhand eines Ausführungsbeispiels näher erläutert.The invention is explained in more detail with reference to an embodiment.
In der Zeichnung zeigen:
-
Fig. 1 in einem Schaltzeichen ein proportional ansteuerbares und in fünf hauptsächliche Schaltstellungen betätigbares Hydraulikventil, -
Fig. 2 eine konstruktive Umsetzung des Hydraulikventils gemäßFig. 1 in einer Schaltstellung, -
Fig. 3 das Hydraulikventil gemäßFig. 2 in einer anderen Schaltstellung, -
Fig. 4 das Hydraulikventil gemäßFig. 2 in einer anderen Schaltstellung, -
Fig. 5 das Hydraulikventil gemäßFig. 2 in einer anderen Schaltstellung und -
Fig. 6 das Hydraulikventil gemäßFig. 2 in einer anderen Schaltstellung,
-
Fig. 1 in a circuit diagram a proportionally controllable and operable in five major switch positions hydraulic valve, -
Fig. 2 a constructive implementation of the hydraulic valve according toFig. 1 in a switching position, -
Fig. 3 the hydraulic valve according toFig. 2 in another switch position, -
Fig. 4 the hydraulic valve according toFig. 2 in another switch position, -
Fig. 5 the hydraulic valve according toFig. 2 in another switch position and -
Fig. 6 the hydraulic valve according toFig. 2 in another switch position,
Vom Hydraulikventil 3 gehen ein erster Verbraucheranschluss A und ein zweiter Verbraucheranschluss B zum Schwenkmotornockenwellenversteller 4 ab. Das Hydraulikventil 3 weist vier Anschlüsse und fünf Schaltstellungen auf und kann somit auch als 4/5-Wege-Ventil mit einer Sperr-Mittelstellung 7 bezeichnet werden. Um den Schwenkmotornockenwellenversteller 4 nun in die erste Drehrichtung 1 zu verschwenken, befindet sich das Hydraulikventil 3 in einer der beiden Schaltstellungen 16, 19, welche durch die beiden Schaltkästchen hinter der Sperr-Mittelstellung 7 dargestellt sind. In der Zeichnung
Umgekehrt gilt analoges. D.h. um den Schwenkmotornockenwellenversteller 4 in die zweite Drehrichtung 2 zu verschwenken, befindet sich das Hydraulikventil 3 in einer der beiden Schaltstellungen 18, 15, welche durch die beiden Schaltkästchen vor der Sperr-Mittelstellung 7 dargestellt sind. In diesen Schaltstellungen 18, 15 werden die dieser Drehrichtung 2 zugeordneten Druckkammern 5 vom zweiten Verbraucheranschluss B mit einem Druck beaufschlagt, der von dem Versorgungsanschluss P kommt. Hingegen werden die der ersten - d.h. entgegen gesetzten - Drehrichtung 1 zugeordneten Druckkammern 6 zum ersten Verbraucheranschluss A hin entlastet. Der erste Verbraucheranschluss A wird dazu über den Tankanschluss T auf den Tank 20 geführt.Conversely, analogous applies. That To pivot the Schwenkmotornockenwellenversteller 4 in the second direction of rotation 2, the
In der besagten Sperr-Mittelstellung 7 werden sämtliche vier Anschlüsse A, B, P, T gesperrt. In den beiden dieser Sperr-Mittelstellung 7 benachbarten Schaltstellungen 15, 16 erfolgt die Verstellung der Nockenwelle ohne Nutzung der Nockenwellenwechselmomente.In the said locking
Dazu ist in der Schaltstellung 15 der Versorgungsanschluss P auf den zweiten Verbraucheranschluss B geführt, wohingegen der erste Versorgungsanschluss A auf den Tankanschluss T geführt ist. Ein Bypass über ein Rückschlagventil ist in dieser Schaltstellung 15 nicht vorgesehen.For this purpose, in the
In der Schaltstellung 16 ist der Versorgungsanschluss P auf den ersten Verbraucheranschluss A geführt, wohingegen der zweite Versorgungsanschluss B auf den Tankanschluss T geführt ist. Ein Bypass über ein Rückschlagventil ist auch in dieser Schaltstellung 15 nicht vorgesehen.In the
In den beiden äußersten Schaltstellungen 18, 19 des Hydraulikventils 3 erfolgt die Verstellung der Nockenwelle mit Nutzung der Nockenwellenwechselmomente. Dazu ist die eine äußerste Schaltstellung 18 ähnlich der unmittelbar benachbarten Schaltstellung 15 ausgeführt. Zudem wird jedoch ein von einem dem ersten Versorgungsanschluss A zugeordnetem Rückschlagventil RSV-A kommender Volumenstrom vom Hydraulikfluid dem Versorgungsanschluss P zur Verfügung gestellt. Hingegen ist die andere äußerste Schaltstellung 19 ähnlich der unmittelbar benachbarten Schaltstellung 16 ausgeführt. Zudem wird jedoch ein von einem dem zweiten Versorgungsanschluss B zugeordnetem Rückschlagventil RSV-B kommender Volumenstrom von Hydraulikfluid dem Versorgungsanschluss P zur Verfügung gestellt.In the two
Dieser zusätzliche Volumenstrom vom zu entlastenden Verbraucheranschluss A bzw. B wird in den von einer Ölpumpe 12 kommenden Volumenstrom am Versorgungsanschluss P eingespeist. Der Versorgungsanschluss P führt dabei über ein Pumpen-Rückschlagventil RSV-P zur Ölpumpe 12, die den Druck zur Verstellung des Schwenkmotornockenwellenverstellers 4 aufbringt. Dieses PumpenRückschlagventil RSV-P sperrt dabei die Drücke im Hydraulikventil 3 ein, so dass von dem zu entlastenden Verbraucheranschluss 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.This additional volume flow from the load connection A or B to be relieved is fed into the volume flow coming from an
Axial zwischen den beiden Außenstegen 23, 24 sind zwei schmale Rippen 31, 32 vorgesehen, die um den Kolben 22 umlaufen. Diese umlaufenden Rippen 31, 32 korrespondieren mit zwei sich von der Buchse 27 radial nach innen erstreckenden Ringstegen 33, 34. Neben diesen beiden Ringstegen 33, 34 sind noch zwei axial äußere Ringstege 35, 36 vorgesehen. Diese vier Ringstege 33 bis 26 bilden sich dabei, da fünf Innenringnuten 37 bis 41 aus der Buchse ausgedreht sind. In diese fünf Innenringnuten 37 bis 41 münden fünf Anschlussbohrungen, welche durch die Wand der Buchse 27 gebohrt sind.Axially between the two
Diese fünf Anschlussbohrungen bilden von Seiten des Elektromagneten 17 axial aufeinander folgend:
- eine dem zweiten Arbeitsanschluss B zugehörige Standardöffnung B1,
- eine dem zweiten Arbeitsanschluss B zugehörige Öffnung B2 zur Nutzung von Nockenwellenwechselmomenten,
- den Versorgungsanschluss P,
- eine dem ersten Arbeitsanschluss A zugehörige Standardöffnung A1 und
- eine dem ersten Arbeitsanschluss A zugehörige Öffnung A2 zur Nutzung von Nockenwellenwechselmomenten.
- a standard opening B1 associated with the second working connection B,
- a second working port B associated opening B2 for the use of camshaft alternating torques,
- the supply terminal P,
- a standard opening A1 and associated with the first working port A.
- a first working port A associated opening A2 for the use of camshaft alternating torques.
An den beiden Arbeitsanschlüssen A, B sind somit jeweils zwei Öffnungen A1, A2 bzw. B1, B2 vorgesehen. Von diesen sind die axial inneren Öffnungen A2, B2 für eine Nockenwellenwechselmomentennutzung vorgesehen. Im Gegensatz zu den ausschließlich mit den Außenstegen 23, 24 von innen sperrbaren axial äußeren Öffnungen A1, B1 weisen die axial inneren Öffnungen A2, B2 die bandförmigen Rückschlagventile RSV-A, RSB-B auf. Jeweils eines der bandförmigen Rückschlagventile RSV-A bzw. RSB-B ist in eine Innenringnut 25 bzw. 26 radial innerhalb der axial inneren Öffnungen A2 bzw. B2 der Buchse 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 28 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 inner annular groove 28. This 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.
In der Schaltstellung 18 gemäß
Der erste Arbeitsanschluss A wird über dessen Standardöffnung A1 und die Querbohrung 30 zum Tankanschluss T geführt bzw. entlastet.The first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
Der erste Arbeitsanschluss A wird über dessen Standardöffnung A1 und die Querbohrung 30 zum Tankanschluss T geführt bzw. entlastetThe first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
Der zweite Arbeitsanschluss B wird über dessen Standardöffnung B1 und die Querbohrung 29 zum Tankanschluss T geführt bzw. entlastetThe second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
Der zweite Arbeitsanschluss B wird über dessen Standardöffnung B1 und die Querbohrung 29 zum Tankanschluss T geführt bzw. entlastet.The second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
In dem dargestellten Ausführungsbeispiel werden die Standardöffnung A1 bzw. B1 und die Öffnung A2 bzw. B2 zur Nutzung von Nockenwellenwechselmomenten erst außerhalb der Buchse 27 zum Arbeitsanschluss A bzw. B zusammengefasst. In alternativen Ausgestaltungsformen ist es auch möglich, die Standardöffnung A1 bzw. B1 und die Öffnung A2 bzw. B2 zur Nutzung von Nockenwellenwechselmomenten bereits innerhalb der Buchse 27 zusammenzuführen. Dazu kann beispielsweise eine Ringnut radial außen in die Buchse eingearbeitet sein.In the illustrated embodiment, the standard opening A1 or B1 and the opening A2 or B2 are summarized for use of camshaft alternating moments only outside the
In einer weiteren alternativen Ausgestaltungsform können anstelle von Bandrückschlagventilen auch Kugelrückschlagventile verwenden werden. So ist es beispielsweise auch möglich, innerhalb des Hydraulikventils Kugelrückschlagventile zu verwenden, wie diese beispielsweise die
Je nach Einsatzbedingungen des Ventils können in Flussrichtung vor einem oder mehreren bzw. sogar allen Anschlüssen auch Siebe vorgesehen sein, welche die Laufflächen zwischen dem Kolben und der Buchse schützen.Depending on the conditions of use of the valve, screens may also be provided in the direction of flow in front of one or more or even all ports, which protect the running surfaces between the piston and the bushing.
Das Hydraulikventil kann auch Anwendung bei einem sogenannten Zentralventil finden. Dabei ist die Buchse nicht mit dem Magnetteil unmittelbar verbunden. Stattdessen ist das Hydraulikventil zentral im Rotor des Schwenkmotornockenwellenverstellers angeordnet, so dass die Buchse gemeinsam mit dem Kolben rotiert. Der Magnet ist hingegen drehfest gegenüber dem Zylinderkopf angeordnet, so dass eine Relativbewegung zwischen dem Stößel des Magnetteils und dem Kolben stattfindet.The hydraulic valve can also find application in a so-called central valve. The socket is not directly connected to the magnetic part. Instead, the hydraulic valve is centrally located in the rotor of the Schwenkmotornockenwellenverstellers so that the sleeve rotates together with the piston. The magnet, however, is rotationally fixed relative to the cylinder head arranged, so that a relative movement between the plunger of the magnetic member and the piston takes place.
Die Nutzung von Nockenwellenwechselmomenten muss nicht für beide Drehrichtungen vorgesehen sein. Es ist auch möglich, auf eine der beiden axial äußersten Schaltstellung 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
In einer alternativen Ausgestaltungsform kann auch für beide Drehrichtung eine Nutzung der Nockenwellenwechselmomente vorgesehen sein, wobei dann jedoch auf eine der beiden die Rückschlagventile RSV-A, RSV-B umgehenden Schaltstellungen 15, 16 verzichtet wird.In an alternative embodiment, a use of the camshaft alternating torques can be provided for both directions, but then to one of the two check valves RSV-A, RSV-B bypassing
Dabei sind beliebige Kombinationen von Schaltstellungen möglich. So ist es möglich, außer der Mittelstellung 7 noch die Schaltstellungen
- 18, 15, 16 oder
- 15, 16, 19 oder
- 18, 15, 19 oder
- 18, 16, 19
- 18, 15, 16 or
- 15, 16, 19 or
- 18, 15, 19 or
- 18, 16, 19
Am Hydraulikventil kann auch noch eine weitere Schaltstellung vorgesehen sein, in der beide Arbeitsanschlüsse A, B gegen den Tankanschluss T entlastet werden, so dass eine sogenannte Mittenverriegelung ermöglicht wird. Bei einer solchen Mittenverriegelung ist im Schwenkmotornockenwellenversteller ein Verriegelungsbolzen vorgesehen, der den Rotor in einer Winkelstellung gegen den Stator festsetzt, welche keine Endlage ist. Eine solche Mittenverriegelung ist beispielsweise in der
Bei den beschriebenen Ausführungsformen handelt es sich nur um beispielhafte Ausgestaltungen. 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.
- 11
- Drehrichtungdirection of rotation
- 22
- Drehrichtungdirection of rotation
- 33
- Hydraulikventilhydraulic valve
- 44
- SchwenkmotornockenwellenverstellerOscillating motor camshaft adjuster
- 55
- Druckkammerpressure chamber
- 66
- Druckkammerpressure chamber
- 77
- Sperr-MittelstellungBlocking center position
- 88th
- WechselmomentenrücklaufanschlussAlternating torque return connection
- 99
- WechselmomentenrücklaufanschlussAlternating torque return connection
- 1010
- TankrücklaufTank return
- 1111
- RückflussleitungReturn line
- 1212
- Ölpumpeoil pump
- 1313
- RückflussleitungReturn line
- 1414
- a, b Ölpumpenleitunga, b oil pump line
- 1515
- Schaltstellungswitch position
- 1616
- Schaltstellungswitch position
- 1717
- Elektromagnetelectromagnet
- 1818
- Schaltstellungswitch position
- 1919
- Schaltstellungswitch position
- 2020
- Tanktank
- 2121
- Federfeather
- 2222
- Kolbenpiston
- 2323
- Außenstegouter web
- 2424
- Außenstegouter web
- 2525
- Innenringnutinner annular
- 2626
- Innenringnutinner annular
- 2727
- BuchseRifle
- 2828
- Innenringnutinner annular
- 2929
- Querbohrungencross holes
- 3030
- Querbohrungencross holes
- 3131
- Ripperib
- 3232
- Ripperib
- 3333
- Ringstegring land
- 3434
- Ringstegring land
- 3535
- Ringstegring land
- 3636
- Ringstegring land
- 3737
- Innenringnutinner annular
- 3838
- Innenringnutinner annular
- 3939
- Innenringnutinner annular
- 4040
- Innenringnutinner annular
- 4141
- Innenringnutinner annular
- AA
- erster Arbeitsanschlussfirst work connection
- A1A1
- erste Standardöffnungfirst standard opening
- A2A2
- erste Öffnung zur Nutzung von Nockenwellenwechselmomentenfirst opening for the use of camshaft alternating torques
- BB
- zweiter Arbeitsanschlusssecond work connection
- B1B1
- zweite Standardöffnungsecond standard opening
- B2B2
- zweite Öffnung zur Nutzung von Nockenwellenwechselmomentensecond opening for the use of camshaft alternating torques
- PP
- Versorgungsanschlusssupply terminal
- TT
- Tankanschlusstank connection
Claims (6)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010014500 | 2010-04-10 | ||
DE102010045358A DE102010045358A1 (en) | 2010-04-10 | 2010-09-14 | Schwenkmotornockenwellenversteller with a hydraulic valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2375014A1 true EP2375014A1 (en) | 2011-10-12 |
EP2375014B1 EP2375014B1 (en) | 2013-07-10 |
Family
ID=44504309
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11157216.0A Active EP2375014B1 (en) | 2010-04-10 | 2011-03-07 | Camshaft phaser comprising a hydraulic valve |
Country Status (5)
Country | Link |
---|---|
US (1) | US8662040B2 (en) |
EP (1) | EP2375014B1 (en) |
JP (1) | JP6025134B2 (en) |
CN (1) | CN102213120B (en) |
DE (1) | DE102010045358A1 (en) |
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DE102010061337A1 (en) | 2010-12-20 | 2012-06-21 | Hydraulik-Ring Gmbh | Hydraulic valve for a Schwenkmotorversteller |
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DE102013104031A1 (en) | 2013-04-22 | 2014-10-23 | Hilite Germany Gmbh | Central valve for a Schwenkmotorversteller |
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US10502128B2 (en) | 2017-05-04 | 2019-12-10 | ECO Holding 1 GmbH | Hydraulic module with switch valve for controlling a hydraulic fluid flow of a connecting rod for an internal combustion engine with variable compression and connecting rod |
DE102019101115A1 (en) | 2018-02-21 | 2019-08-22 | ECO Holding 1 GmbH | Hydraulic valve for a Schwenkmotorversteller a camshaft |
DE102019101159A1 (en) | 2018-02-21 | 2019-08-22 | ECO Holding 1 GmbH | Hydraulic valve for a Schwenkmotorversteller a camshaft |
EP3530892A1 (en) | 2018-02-21 | 2019-08-28 | ECO Holding 1 GmbH | Hydraulic valve for a pivoting engine adjuster of a camshaft |
EP3530891A1 (en) | 2018-02-21 | 2019-08-28 | ECO Holding 1 GmbH | Hydraulic valve for a pivoting engine adjuster of a camshaft |
US11111826B2 (en) | 2018-02-21 | 2021-09-07 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
US11300017B2 (en) | 2018-02-21 | 2022-04-12 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
CN112302752A (en) * | 2019-07-25 | 2021-02-02 | 句容嘉晟汽车配件有限公司 | VVT system |
Also Published As
Publication number | Publication date |
---|---|
EP2375014B1 (en) | 2013-07-10 |
JP2011226474A (en) | 2011-11-10 |
CN102213120B (en) | 2013-06-05 |
US8662040B2 (en) | 2014-03-04 |
JP6025134B2 (en) | 2016-11-16 |
CN102213120A (en) | 2011-10-12 |
US20110247576A1 (en) | 2011-10-13 |
DE102010045358A1 (en) | 2011-10-13 |
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