EP3170997B1 - Variable valve drive with a rocker arm - Google Patents
Variable valve drive with a rocker arm Download PDFInfo
- Publication number
- EP3170997B1 EP3170997B1 EP16002314.9A EP16002314A EP3170997B1 EP 3170997 B1 EP3170997 B1 EP 3170997B1 EP 16002314 A EP16002314 A EP 16002314A EP 3170997 B1 EP3170997 B1 EP 3170997B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rocker arm
- cam
- roller lever
- pin
- camshaft
- 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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- 238000013461 design Methods 0.000 claims description 4
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- 241000406668 Loxodonta cyclotis Species 0.000 claims description 2
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
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- 238000010079 rubber tapping Methods 0.000 description 1
- 238000012549 training Methods 0.000 description 1
- 210000000707 wrist Anatomy 0.000 description 1
Images
Classifications
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
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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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
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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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
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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
- F01L1/12—Transmitting gear between valve drive and valve
-
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
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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
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0203—Variable control of intake and exhaust valves
- F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
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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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
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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
- F01L2305/00—Valve arrangements comprising rollers
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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
- F01L2305/00—Valve arrangements comprising rollers
- F01L2305/02—Mounting of rollers
-
- 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
- F01L2820/03—Auxiliary actuators
- F01L2820/033—Hydraulic engines
Definitions
- the invention relates to a variable valve train for a lift valve, in particular for a charge exchange valve of an internal combustion engine, which is periodically movable between a closed and an open position by a cam via a rocker arm.
- variable valve trains offer the advantageous possibility of targeted adjustment of the course of the valve lift over the cam angle as a function of operating parameters of the device equipped with the respective lift valve, that is, for example, depending on the speed, load or temperature of an internal combustion engine.
- a camshaft block with two different cam contours is rotatably but axially displaceably arranged on a camshaft. According to the axial position of the cam block is a cam contour via an intermediate member (transmission lever) with the lifting valve in operative connection. The axial displacement of the cam block to change the valve parameters takes place during the Grundnikphase against the action of a return spring by means of a pressure ring.
- a disadvantage of the cited prior art is the high space requirement, which is required for adjusting the cam block or for the axial adjustment of the camshaft.
- a rocker arm assembly for a variable valve train wherein a first rocker arm of each rocker arm is associated with a cam with a small cam lift and a second rocker cam with a large cam lift, each with a locking device for each pair of rocker, through which only the larger cam lift when switched on having cam for both rocker arm is effective.
- a disadvantage of this known valve train is the need for an external spring stop to ensure the return of the second rocker arm. This and the independent storage of the second rocker arm also allow no pre-assembly.
- the two levers need a driving point, which leads to the fact that the two cam profiles must be symmetrical to each other or the apex of the two cams have no angular offset from each other. This prevents the possibility of varying the phase position of the valve lifts.
- US Pat. No. 7,311,073 B1 a variable valve train for a finger follower arrangement, wherein the adjustment of the valve lift takes place via a plurality of cams with different cam contours via a transmission element additionally mounted between the camshaft and the valve lever.
- This one is on an additional one Shaft pivotally mounted transfer rocker arm, which is in operative contact with a second eccentrically mounted to the additional shaft transfer rocker arm over a contour surface.
- By rotating the additional shaft changes due to the eccentricity of the contact area on the contour surface and thus the transmitted to the valve stroke.
- a disadvantage of this arrangement are the number of additional components for the transmission mechanism and the additional space requirement.
- variable valve train with a rocker arm, with which disadvantages of conventional techniques can be avoided.
- the invention is based in particular on the object of a structurally compact and easy-to-install design of such a variable valve train.
- a variable valve drive is provided for a lift valve.
- the lift valve is between a closed and an open position, in particular against the force of a return spring, indirectly movable by a cam of a camshaft via a rocker arm periodically.
- the lift valve is preferably a charge exchange valve of an internal combustion engine.
- the valve train comprises a camshaft, comprising at least one first cam and at least one offset in the longitudinal direction of the camshaft second cam, wherein the at least one first cam and the at least one second cam are designed differently in their cam contour.
- the cam contour of the at least one first cam to the cam contour of the at least one second cam may have a different cam lobe and / or a different phase position.
- the at least one second cam has a larger cam lift (cam lift) than the at least one first cam.
- the cam contours each determine, taking into account the valve clearance according to their training, the opening and closing time and / or the opening stroke of the lift valve.
- a second cam may be disposed immediately adjacent to a first cam.
- the valve drive further comprises a rocker arm mounted pivotably about a rocker arm axis, which is assigned at its camshaft-side end via a roller, in particular a pressure roller, of the first cam and is in operative connection with the lift valve at its valve-side end.
- a rocker arm mounted pivotably about a rocker arm axis, which is assigned at its camshaft-side end via a roller, in particular a pressure roller, of the first cam and is in operative connection with the lift valve at its valve-side end.
- One arm of the rocker arm thus serves to actuate the lift valve, the other lever arm is driven by a cam.
- the rocker arm is preferably mounted on a central region on the rocker shaft.
- the valve drive further comprises a roller lever which is assigned at its camshaft-side end to the at least one second cam via at least one roller, d. H. the movement of the / the second cam (s) picks up, and is articulated at its other end on the rocker arm about the rocker arm pivotally.
- valvetrain comprises a switchable hydraulic locking means by which the rocker arm and the roller lever can be selectively locked together, wherein rocker arms and roller levers follow the movement of the at least one second cam or can be unlocked from each other, wherein rocker arms and roller levers are independently rotatable and both independently follow the respective associated cam.
- the second cam In the unlocked state, the second cam is ineffective - it actuates the roller lever, but only performs tilting movements, without influencing the valve.
- Rocker arm and roller lever rotatably connected to each other, so that both can only be pivoted together about the rocker arm axis.
- a particular advantage of the valve drive according to the invention lies in the compact design, which does not or at least hardly affects the space in height and length of a conventional toggle lever-based valve train.
- the rocker arm only becomes wider, but moves in the size range of a conventional two-valve rocker arm.
- the invention makes it possible to convert an existing valve train without variability, without requiring changes to surrounding components, apart from those which are needed directly for the realization of the variability.
- Another advantage is in particular that no changes to the cylinder head are necessary if a conventional non-variable rocker arm valve drive is to be replaced by the variable valve train according to the invention.
- the roller lever is formed so that it has two arms which extend on both sides of the camshaft-side end of the rocker arm and tap the cam contour of the two second cam. The two arms engage their associated second cam each with a roller, z. B. a pressure roller from, which rolls on the second cam.
- This two-armed embodiment of the roller lever allows an advantageous power flow to transmit the cam movement of the second cam in the activated state of the hydraulic locking device via the roller lever on the rocker arm and the rocker arm to the lift valve.
- the camshaft side end of the rocker arm may be provided on both sides of the second cam ever a first cam and the camshaft side end of the rocker arm extend on both sides of the roller lever and tap the cam contour of the two first cam.
- the camshaft end of the rocker arm thus has two arms, wherein the roller lever is arranged therebetween. The two arms grasp their associated first cam each with a roller, z. B. a pressure roller from, which rolls on the first cam.
- the roller lever is connected to the rocker arm via a hinge for rotatably securing the roller lever to the rocker arm about the rocker arm axis.
- the rocker arm and the roller lever each have a hinge pin receptacle, which are arranged in alignment with each other and have an inserted hinge pin.
- a further advantageous possibility of the realization according to the invention provides that the rocker arm and the roller lever are clamped together by at least one return spring, such that the rollers of roller lever and rocker arm are aligned in a base circle position to each other.
- the roller lever is pressed by the return spring permanently to the main rocker arm while the camshaft is in a base circle position.
- These return springs preferably press on a contact point on or of the rocker arm and on a contact point on or of the roller lever. Due to the mutual tension easy pre-assembly of the entire switchable rocker arm is possible. It when two such return springs - seen in the longitudinal direction of the rocker arm - are arranged on both sides of the rocker arm is particularly advantageous.
- the switchable hydraulic locking device comprises a hydraulically actuable shift pin, which can be brought from a first position (release position) in a second position (locking position) by applying a predetermined hydraulic pressure.
- the shift pin prevents a relative movement of the rocker arm to the roller lever to each other about the Kipphebelachse, d. h.
- the roller lever can not be pivoted independently of the rocker arm about the tilt axis.
- the rocker arm and the roller lever are hydraulically locked, but not in the first position.
- this embodiment are in the rocker arm in a Gleit Resultssbohrung the rocker arm, a guide pin, a plugged onto the guide pin bolt spring and the shift pin of the hydraulic Verrieglungs noticed, which is bolted to the guide pin arranged.
- the switching pin is on one for actuation the circuit can be filled with oil-filled pressure chamber with a predetermined oil pressure.
- the locking direction can be designed according to a first variant so that the switching pin is held in a state not acted upon by the predetermined pressure by acting as a return spring bolt spring and the guide pin in the first position and in a state acted upon by the predetermined pressure in the second position is pressed, in which the switching pin protrudes from the rocker arm in the direction of the roller lever and moves into an aligned Gleit Unitsam the roller lever.
- the locking direction can be further designed according to a second variant, that the switching pin is held in a state not acted upon by the predetermined pressure by the bolt spring in the second position (locking position), so that roller lever and rocker arms are locked together rotatably and in one pressed state with the predetermined pressure are pressed into the first position in which the shift pin is sunk into the rocker arm and the two levers are unlocked from each other.
- roller lever is designed to be open, so that the compressed by the retraction of the shift pin compressed air can escape and does not resist the extension movement of the shift pin. This opening is already provided in the blank of the roller lever, so that no additional vent hole is needed.
- the rocker arm can on its underside, d. H. the cylinder head facing side, have a geometry for axial fixation on a bearing block.
- the rocker arm may have a mounting for attachment to a Kipphebellagerbock on which the rocker shaft is arranged, on which the rocker arm with an associated bore is pivotally mounted and held by an axial position assurance, wherein the axial position securing a guide connection as an engagement element counter-element connection between the bearing block and the rocker arm, in which a transversely aligned to the axial direction engagement element, for. B. in the form of an annular web, engages pivotally in an associated counter element with axial flank support.
- Another aspect of the invention relates to a motor vehicle, in particular a commercial vehicle, with a variable valve train, as described in this document.
- FIGS. 1 to 3 show various perspective views of a variable valve train 1 according to an embodiment of the invention.
- the valve train 1 is used to actuate a charge exchange valve (not shown) of an internal combustion engine which is periodically movable between a closed and an open position by a cam via a rocker arm.
- the camshaft 7 has a central cam 3, also referred to as first cam in this document, and two further cams 4, 5 arranged staggered in the longitudinal direction of the camshaft 7. These cams 4, 5 are also referred to as second cams in this document , The two cams 4, 5 are arranged on both sides of the central cam and adjacent to this. The central cam 3 and the two second cams 4, 5 are designed differently in their cam contour. The second cams 4, 5 have a larger cam lift than the middle cam 3.
- phase angle of the central cam 3 with respect to the second cam 4, 5 may differ.
- the first cam may also be designed as a zero cam, so that the valves remain closed.
- the valve train further comprises a rocker arm assembly comprising a rocker arm 10 pivotably mounted about a rocker shaft 2 and associated with its camshaft end 11 via a pressure roller 13 of the first cam 3 for tapping it and at its valve end 12 in operative communication with at least one Lift valve is stopped.
- a rocker arm assembly comprising a rocker arm 10 pivotably mounted about a rocker shaft 2 and associated with its camshaft end 11 via a pressure roller 13 of the first cam 3 for tapping it and at its valve end 12 in operative communication with at least one Lift valve is stopped.
- rocker arm 10 is mounted on a rocker arm bearing block (not shown), wherein the rocker arm 2 is disposed on the rocker arm bearing block, on which the rocker arm 10 is pivotally mounted with an associated bore and held by an axial position assurance.
- the axial position assurance can be done for example in a conventional manner via contact surfaces on the Kipphebelflanken. These flanks can be created for example by calibration of the forging blank or by mechanical processing. Bearing side, the fixation can also be done on appropriately machined surfaces and by means of washers and retaining rings.
- Next axial position locks between a rocker arm and the axle are known. For example, has an area of the axis, which is enclosed by the bore of the rocker arm, an annular groove in which a snap ring extends, which runs at the same time with its outer ring portion in an annular groove of the rocker arm
- the axial position assurance is designed as an engagement element counter-element connection between the bearing block and the rocker arm, wherein a transversely aligned to the axial direction engagement element, for. B. in the form of an annular web 16, in an associated counter-element (not shown) engages pivotally with axial flank support.
- the valve-side lever arm 12 of the rocker arm 10 is designed as a two-valve lever arm to actuate two charge exchange valves simultaneously.
- the valve-side lever arm 12 is fork-shaped.
- a Recording 15 arranged at each valve-side end of the lever arm 12 .
- the receptacle 15 can be used for mounting a known hydraulic valve lash adjuster element (not shown). Instead of a hydraulic valve clearance compensation element, a screw with elephant foot can be accommodated in the receptacle 15, by means of which a valve clearance can be readjusted manually.
- Hydraulic valve clearance compensation elements in internal combustion engines are known per se and serve, in particular, to compensate for the change over the operating length length dimensions of the charge exchange valves so that in the base circle phase of the valve-actuating cam secure valve closing is ensured. On the other hand, the cam lobe should be transferred without loss to the valve and thus converted into a valve lift.
- the operation of such hydraulic valve clearance compensation elements which are arranged in the power flow of a valve control, in particular an internal combustion engine, is assumed to be known.
- valve train 1 further comprises a roller lever 20, which is assigned to the two second cams 4, 5 at its camshaft-side end 21 and is pivoted at its other end to the rocker arm 10 about the rocker shaft 2.
- the rocker arm 10 is connected via a hinge pin 25 rotatably connected to the roller lever 20.
- a hinge pin receptacle 14 For this connection is located on the rocker arm 10 is a hinge pin receptacle 14 and the roller lever 20 is a hinge pin receptacle 24.
- the mutually aligned hinge pin receptacles 14, 24 are on an upper side, d. H. a side facing away from the cylinder head, the rocking lever 10, and that at a central region of the rocker arm 10, which forms the cylindrical recess of the rocker arm, in which the rocker shaft 2 is received.
- the camshaft side lever arm 11 of the rocker arm 10 carries at its end a pressure roller 13 which is associated with the central cam 3 to tap the cam 3 and its rotational movement.
- the roller lever has two to the camshaft / down extending, parallel arms 21, which also - in the longitudinal direction of the camshaft / seen - on different sides of the camshaft side lever arm 11 of the rocker arm 10 extend.
- Each of the two arms 21 also carries at the end a pressure roller 23.
- Each of the pressure rollers 23 is one of the two second cams 4, 5 assigned to tap these.
- Both the rocker arm 10 and the roller lever 20 are thus rotatably mounted to the rocker shaft 2 and independently pivotable to the rocker arm axis - at least when rocker arm 10 and roller lever 20 are not locked together by the switchable hydraulic locking device.
- a basic circle phase or cam base circle phase is to be understood as meaning, in particular, an angular range of the cam unit in which cam contours of all partial cams of the cam unit occupy a common base circle level.
- variable valve train 1 further comprises a switchable hydraulic locking device or a hydraulic switching element 30, are locked by the rigidly with each other when switching the rocker arm 10 and the roller lever 20 and both of the movement of the second cam 4, 5 follow.
- the switchable hydraulic locking device 30 comprises a guide pin 34, on which a bolt spring 33 is attached.
- the guide pin 34 and the bolt spring 33 are located in a Gleit Resultssbohrung 37, which is introduced into the camshaft-side lever arm 11 of the rocker arm 10.
- Gleit Resultssbohrung 37 of the guide pin 34 is screwed to a shift pin 31.
- the bolt spring 34 comes to a spring stop 32 to the plant.
- the switching pin 31 also has a zero point system 36. In a basic state (no pressurization), the switching pin 31 is pressed by the bolt spring 33 to the zero point system 36. Behind the switching pin 31 is a pressure chamber 35, which is filled to actuate the circuit with oil.
- Rocker arm 10 and roller lever 20 are thus rotatably supported independently of each other about the Kipphebelachse 2 when not switched hydraulic locking direction 30, so that the second cam 4, 5 are ineffective, d. that is, the second cams 4, 5 actuate the roller lever 20, but only performs tilting movements, without influencing the valve.
- the rocker arm and roller lever are rotatably connected to each other when the locking direction is switched on, so that both can only be pivoted together about the rocker shaft axis 2.
Description
Die Erfindung betrifft einen variablen Ventiltrieb für ein Hubventil, insbesondere für ein Ladungswechselventil einer Brennkraftmaschine, das zwischen einer Schließ- und einer Öffnungsstellung mittelbar durch einen Nocken über einen Kipphebel periodisch bewegbar ist.The invention relates to a variable valve train for a lift valve, in particular for a charge exchange valve of an internal combustion engine, which is periodically movable between a closed and an open position by a cam via a rocker arm.
Es ist bekannt, Gaswechselventile einer Brennkraftmaschine variabel mit unterschiedlichen Öffnungs- und Schließzeitpunkten sowie mit unterschiedlichen Ventilöffnungshüben zu betreiben. Derartige variable Ventiltriebe bieten die vorteilhafte Möglichkeit der gezielten Anpassung des Verlaufes der Ventilhubkurve über dem Nockenwinkel in Abhängigkeit von Betriebsparametern der mit dem jeweiligen Hubventil ausgestatteten Einrichtung, also beispielsweise in Abhängigkeit von Drehzahl, Last oder Temperatur einer Brennkraftmaschine.It is known to operate gas exchange valves of an internal combustion engine variable with different opening and closing times and with different valve opening strokes. Such variable valve trains offer the advantageous possibility of targeted adjustment of the course of the valve lift over the cam angle as a function of operating parameters of the device equipped with the respective lift valve, that is, for example, depending on the speed, load or temperature of an internal combustion engine.
Es ist insbesondere bekannt, mehrere unterschiedliche Hubkurven für ein Hubventil dadurch zu erzeugen, dass zur Betätigung dieses Hubventils mehrere Nocken vorhanden sind und dass jeweils die Kontur nur eines Nockens den Hubverlauf bewirkt. Zur Umschaltung auf einen anderen Hubverlauf wird auf die Kontur eines anderen Nockens umgeschaltet. Eine derartige Ventilsteuerung ist aus der
Aus der
Weiterhin ist aus der
Nachteilig bei dem zitierten Stand der Technik ist der hohe Bauraumbedarf, der zur Verstellung des Nockenblocks bzw. zur axialen Verstellung der Nockenwelle benötigt wird.A disadvantage of the cited prior art is the high space requirement, which is required for adjusting the cam block or for the axial adjustment of the camshaft.
Ferner ist aus der
Ähnliche Ausführungen mit wahlweise aneinander kuppelbaren Kipphebeln, die jeweils mit verschieden geformten Nocken zusammenwirken, sind auch aus der
Die Patentschrift
Ferner offenbart die
Es ist eine Aufgabe der Erfindung, einen verbesserten variablen Ventiltrieb mit einem Kipphebel bereitzustellen, mit dem Nachteile herkömmlicher Techniken vermieden werden können. Der Erfindung liegt insbesondere die Aufgabe einer baulich kompakten und einfach zu montierenden Gestaltung eines solchen variablen Ventiltriebs zugrunde.It is an object of the invention to provide an improved variable valve train with a rocker arm, with which disadvantages of conventional techniques can be avoided. The invention is based in particular on the object of a structurally compact and easy-to-install design of such a variable valve train.
Diese Aufgaben werden durch einen variablen Ventiltrieb mit den Merkmalen des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen und Anwendungen der Erfindung sind Gegenstand der abhängigen Ansprüche und werden in der folgenden Beschreibung unter teilweiser Bezugnahme auf die Figuren näher erläutert.These objects are achieved by a variable valve train with the features of the independent claim. Advantageous embodiments and applications of the invention are the subject matter of the dependent claims and are explained in more detail in the following description with partial reference to the figures.
Erfindungsgemäß wird ein variabler Ventiltrieb für ein Hubventil bereitgestellt. Das Hubventil ist zwischen einer Schließ- und einer Öffnungsstellung, insbesondere entgegen der Kraft einer Rückstellfeder, mittelbar durch einen Nocken einer Nockenwelle über einen Kipphebel periodisch bewegbar. Das Hubventil ist vorzugsweise ein Ladungswechselventil einer Brennkraftmaschine.According to the invention, a variable valve drive is provided for a lift valve. The lift valve is between a closed and an open position, in particular against the force of a return spring, indirectly movable by a cam of a camshaft via a rocker arm periodically. The lift valve is preferably a charge exchange valve of an internal combustion engine.
Gemäß allgemeinen Gesichtspunkten der Erfindung umfasst der Ventiltrieb eine Nockenwelle, aufweisend mindestens einen ersten Nocken und mindestens einen in Längsrichtung der Nockenwelle versetzt angeordneten zweiten Nocken, wobei der mindestens eine erste Nocken und der mindestens eine zweite Nocken in ihrer Nockenkontur unterschiedlich gestaltet sind. Beispielsweise kann die Nockenkontur des mindestens einen ersten Nockens zu der Nockenkontur des mindestens einen zweiten Nockens eine unterschiedliche Nockenerhebung und/oder eine unterschiedliche Phasenlage aufweisen. Vorzugsweise weist der mindestens eine zweite Nocken eine größere Nockenerhebung (Nockenhub) als der mindestens eine erste Nocken auf.According to general aspects of the invention, the valve train comprises a camshaft, comprising at least one first cam and at least one offset in the longitudinal direction of the camshaft second cam, wherein the at least one first cam and the at least one second cam are designed differently in their cam contour. For example, the cam contour of the at least one first cam to the cam contour of the at least one second cam may have a different cam lobe and / or a different phase position. Preferably, the at least one second cam has a larger cam lift (cam lift) than the at least one first cam.
Die Nockenkonturen bestimmen jeweils unter Berücksichtigung des Ventilspiels entsprechend ihrer Ausbildung den Öffnungs- und Schließzeitpunkt und/oder den Öffnungshub des Hubventils. Ein zweiter Nocken kann unmittelbar benachbart zu einem ersten Nocken angeordnet sein.The cam contours each determine, taking into account the valve clearance according to their training, the opening and closing time and / or the opening stroke of the lift valve. A second cam may be disposed immediately adjacent to a first cam.
Der Ventiltrieb umfasst ferner einen um eine Kipphebelachse verschwenkbar gelagerten Kipphebel, der an seinem nockenwellenseitigen Ende über eine Rolle, insbesondere eine Druckrolle, des ersten Nockens zugeordnet ist und an seinem ventilseitigen Ende in Wirkverbindung mit dem Hubventil steht. Ein Arm des Kipphebels dient somit zur Betätigung des Hubventils, der andere Hebelarm wird durch einen Nocken angetrieben. Der Kipphebel ist vorzugsweise an einem mittleren Bereich an der Kipphebelachse gelagert.The valve drive further comprises a rocker arm mounted pivotably about a rocker arm axis, which is assigned at its camshaft-side end via a roller, in particular a pressure roller, of the first cam and is in operative connection with the lift valve at its valve-side end. One arm of the rocker arm thus serves to actuate the lift valve, the other lever arm is driven by a cam. The rocker arm is preferably mounted on a central region on the rocker shaft.
Der Ventiltrieb umfasst ferner einen Rollenhebel, der an seinem nockenwellenseitigen Ende dem mindestens einen zweiten Nocken über mindestens eine Rolle zugeordnet ist, d. h. die Bewegung des/der zweiten Nocken(s) abgreift, und an seinem anderen Ende am Kipphebel um die Kipphebelachse verschwenkbar angelenkt ist.The valve drive further comprises a roller lever which is assigned at its camshaft-side end to the at least one second cam via at least one roller, d. H. the movement of the / the second cam (s) picks up, and is articulated at its other end on the rocker arm about the rocker arm pivotally.
Ferner umfasst der Ventiltrieb eine schaltbare hydraulische Verriegelungseinrichtung, durch die der Kipphebel und der Rollenhebel wahlweise starr miteinander verriegelt werden können, wobei Kipphebel und Rollenhebel der Bewegung des mindestens einen zweiten Nockens folgen oder voneinander entriegelt werden können, wobei Kipphebel und Rollenhebel unabhängig voneinander drehbar sind und beide unabhängig voneinander den jeweilig zugeordneten Nocken folgen. Im entriegelten Zustand ist der zweite Nocken unwirksam - er betätigt zwar den Rollenhebel, der aber nur Kippbewegungen ausführt, ohne Einflussnahme auf das Ventil. Dagegen sind im durch die Verriegelungseinrichtung verriegelten Zustand Kipphebel und Rollenhebel drehfest miteinander verbunden, so dass beide nur gemeinsam um die Kipphebelachse verschwenkbar sind.Further, the valvetrain comprises a switchable hydraulic locking means by which the rocker arm and the roller lever can be selectively locked together, wherein rocker arms and roller levers follow the movement of the at least one second cam or can be unlocked from each other, wherein rocker arms and roller levers are independently rotatable and both independently follow the respective associated cam. In the unlocked state, the second cam is ineffective - it actuates the roller lever, but only performs tilting movements, without influencing the valve. On the other hand, in the locked by the locking device state Rocker arm and roller lever rotatably connected to each other, so that both can only be pivoted together about the rocker arm axis.
Ein besonderer Vorzug des erfindungsgemäßen Ventiltriebs liegt in der kompakten Bauweise, welche den Bauraum in Höhe und Länge eines herkömmlichen kipphebelbasierten Ventiltriebs nicht oder zumindest kaum beeinflusst. Der Kipphebel wird lediglich breiter, bewegt sich jedoch im Größenrahmen eines üblichen Zwei-Ventil-Kipphebels. Dadurch, dass der Rollenhebel direkt am Kipphebel schwenkbar befestigt wird, kann die Kipphebelanordnung aus Kipphebel und Rollenhebel bereits vormontiert als Einheit verwendet werden, wodurch die Montageaufwände reduziert werden können. Ebenso ermöglicht die Erfindung, einen bestehenden Ventiltrieb ohne Variabilität umzurüsten, ohne dabei Änderungen an umliegenden Bauteile zu erfordern, abgesehen von denen, welche unmittelbar für die Realisierung der Variabilität benötigt werden. Ein weiterer Vorteil liegt insbesondere darin, dass keine Änderungen am Zylinderkopf notwendig sind, falls ein herkömmlicher nicht-variabler Kipphebelventiltrieb durch den erfindungsgemäßen variablen Ventiltrieb ersetzt werden soll.A particular advantage of the valve drive according to the invention lies in the compact design, which does not or at least hardly affects the space in height and length of a conventional toggle lever-based valve train. The rocker arm only becomes wider, but moves in the size range of a conventional two-valve rocker arm. Characterized in that the roller lever is pivotally mounted directly on the rocker arm, the rocker arm assembly of rocker arm and roller lever can be pre-assembled as a unit, whereby the assembly costs can be reduced. Likewise, the invention makes it possible to convert an existing valve train without variability, without requiring changes to surrounding components, apart from those which are needed directly for the realization of the variability. Another advantage is in particular that no changes to the cylinder head are necessary if a conventional non-variable rocker arm valve drive is to be replaced by the variable valve train according to the invention.
Gemäß einer bevorzugten Ausgestaltungsform ist beidseitig von dem ersten Nocken - in Längsrichtung der Nockenwelle gesehen - je ein zweiter Nocken vorgesehen, d. h. ein Nocken mit einer von dem mittleren ersten Nocken unterschiedlichen Nockenkontur. Entsprechend ist der Rollenhebel so ausgebildet, dass er zwei Arme aufweist, die sich beidseitig vom nockenwellenseitigen Ende des Kipphebels erstrecken und die Nockenkontur der beiden zweiten Nocken abgreifen. Die beiden Arme greifen den ihnen zugeordneten zweiten Nocken jeweils mit einer Rolle, z. B. einer Druckrolle, ab, die auf dem zweiten Nocken abrollt. Diese zweiarmige Ausführung des Rollenhebels ermöglicht einen vorteilhaften Kraftfluss, um die Nockenbewegung der zweiten Nocken im zugeschalteten Zustand der hydraulischen Verriegelungseinrichtung über den Rollenhebel auf den Kipphebel und über den Kipphebel auf das Hubventil zu übertragen.According to a preferred embodiment, on both sides of the first cam - seen in the longitudinal direction of the camshaft - each provided a second cam, d. H. a cam with a different from the middle first cam cam contour. Accordingly, the roller lever is formed so that it has two arms which extend on both sides of the camshaft-side end of the rocker arm and tap the cam contour of the two second cam. The two arms engage their associated second cam each with a roller, z. B. a pressure roller from, which rolls on the second cam. This two-armed embodiment of the roller lever allows an advantageous power flow to transmit the cam movement of the second cam in the activated state of the hydraulic locking device via the roller lever on the rocker arm and the rocker arm to the lift valve.
Gemäß einer alternativen Ausgestaltungsform kann beidseitig von dem zweiten Nocken je ein erster Nocken vorgesehen sein und das nockenwellenseitige Ende des Kipphebels sich beidseitig vom Rollenhebel erstrecken und die Nockenkontur der beiden ersten Nocken abgreifen. Bei dieser alternativen Ausgestaltungsform weist das nockenwellenseitige Ende des Kipphebels somit zwei Arme auf, wobei der Rollenhebel dazwischen angeordnet ist. Die beiden Arme greifen den ihnen zugeordneten ersten Nocken jeweils mit einer Rolle, z. B. einer Druckrolle, ab, die auf dem ersten Nocken abrollt.According to an alternative embodiment may be provided on both sides of the second cam ever a first cam and the camshaft side end of the rocker arm extend on both sides of the roller lever and tap the cam contour of the two first cam. In this alternative embodiment, the camshaft end of the rocker arm thus has two arms, wherein the roller lever is arranged therebetween. The two arms grasp their associated first cam each with a roller, z. B. a pressure roller from, which rolls on the first cam.
Gemäß einer ersten Alternative der Erfindung ist der Rollenhebel mit dem Kipphebel über ein Scharnier verbunden, um den Rollenhebel am Kipphebel um die Kipphebelachse drehbar zu befestigen. Gemäß einer zweiten Alternative der Erfindung weist der Kipphebel und der Rollenhebel jeweils eine Gelenkstiftaufnahme auf, die zueinander fluchtend angeordnet sind und einen eingesetzten Gelenkstift aufweisen.According to a first alternative of the invention, the roller lever is connected to the rocker arm via a hinge for rotatably securing the roller lever to the rocker arm about the rocker arm axis. According to a second alternative of the invention, the rocker arm and the roller lever each have a hinge pin receptacle, which are arranged in alignment with each other and have an inserted hinge pin.
Eine weitere vorteilhafte Möglichkeit der erfindungsgemäßen Realisierung sieht vor, dass der Kipphebel und der Rollenhebel über mindestens eine Rückstellfeder miteinander verspannt sind, derart, dass die Rollen von Rollenhebel und Kipphebel in einer Grundkreisstellung zueinander fluchten. Mit anderen Worten wird der Rollenhebel durch die Rückstellfeder permanent an den Hauptkipphebel gedrückt, während die Nockenwelle sich in einer Grundkreisstellung befindet.A further advantageous possibility of the realization according to the invention provides that the rocker arm and the roller lever are clamped together by at least one return spring, such that the rollers of roller lever and rocker arm are aligned in a base circle position to each other. In other words, the roller lever is pressed by the return spring permanently to the main rocker arm while the camshaft is in a base circle position.
Diese Rückstellfedern drücken dabei vorzugsweise auf eine Anlagestelle am bzw. des Kipphebels und auf eine Anlagestelle am bzw. des Rollenhebels. Durch die gegenseitige Verspannung ist eine leichte Vormontage des gesamten schaltbaren Kipphebels möglich. Besonders vorteilhaft ist es, wenn zwei derartige Rückstellfedern - in Längsrichtung der Kipphebelachse gesehen - beidseitig vom Kipphebel angeordnet sind.These return springs preferably press on a contact point on or of the rocker arm and on a contact point on or of the roller lever. Due to the mutual tension easy pre-assembly of the entire switchable rocker arm is possible. It when two such return springs - seen in the longitudinal direction of the rocker arm - are arranged on both sides of the rocker arm is particularly advantageous.
Gemäß einer bevorzugten Ausgestaltungsform umfasst die schaltbare hydraulische Verriegelungseinrichtung einen hydraulisch betätigbaren Schaltbolzen, der durch Beaufschlagung mit einem vorbestimmten hydraulischen Druck von einer ersten Stellung (Freigabestellung) in eine zweite Stellung (Verriegelungsstellung) bringbar ist. In der zweiten Stellung verhindert der Schaltbolzen eine Relativbewegung des Kipphebels zum Rollenhebel zueinander um die Kipphebelachse, d. h., in der zweiten Stellung kann der Rollenhebel nicht mehr unabhängig vom Kipphebel um die Kippachse verschwenkt werden. In der ersten Stellung lässt der Schaltbolzen eine Relativbewegung des Kipphebels und des Rollenhebels zueinander zu. In der zweiten Stellung sind der Kipphebel und der Rollenhebel hydraulisch verriegelt, in der ersten Stellung dagegen nicht.According to a preferred embodiment, the switchable hydraulic locking device comprises a hydraulically actuable shift pin, which can be brought from a first position (release position) in a second position (locking position) by applying a predetermined hydraulic pressure. In the second position, the shift pin prevents a relative movement of the rocker arm to the roller lever to each other about the Kipphebelachse, d. h., In the second position, the roller lever can not be pivoted independently of the rocker arm about the tilt axis. In the first position of the shift pin allows a relative movement of the rocker arm and the roller lever to each other. In the second position, the rocker arm and the roller lever are hydraulically locked, but not in the first position.
Gemäß einer vorteilhaften Variante dieser Ausgestaltungsform sind im Kipphebel in einer Gleitführungsbohrung des Kipphebels ein Führungsbolzen, eine auf den Führungsbolzen gesteckte Bolzenfeder und der Schaltbolzen der hydraulischen Verrieglungseinrichtung, der mit dem Führungsbolzen verschraubt ist, angeordnet. Der Schaltbolzen ist über eine zur Betätigung der Schaltung mit Öl befüllbare Druckkammer mit einem vorbestimmten Öldruck beaufschlagbar.According to an advantageous variant of this embodiment are in the rocker arm in a Gleitführungsbohrung the rocker arm, a guide pin, a plugged onto the guide pin bolt spring and the shift pin of the hydraulic Verrieglungseinrichtung, which is bolted to the guide pin arranged. The switching pin is on one for actuation the circuit can be filled with oil-filled pressure chamber with a predetermined oil pressure.
Hierbei kann die Verriegelungsrichtung gemäß einer ersten Variante so ausgeführt sein, dass der Schaltbolzen in einem nicht mit dem vorbestimmten Druck beaufschlagten Zustand durch die als Rückstellfeder wirkende Bolzenfeder und den Führungsbolzen in der ersten Stellung gehalten wird und in einem mit dem vorbestimmten Druck beaufschlagten Zustand in die zweite Stellung gedrückt wird, in der der Schaltbolzen aus dem Kipphebel in Richtung der Rollenhebels herausragt und in eine fluchtende Gleitführungsaufnahme des Rollenhebels einfährt.In this case, the locking direction can be designed according to a first variant so that the switching pin is held in a state not acted upon by the predetermined pressure by acting as a return spring bolt spring and the guide pin in the first position and in a state acted upon by the predetermined pressure in the second position is pressed, in which the switching pin protrudes from the rocker arm in the direction of the roller lever and moves into an aligned Gleitführungsaufnahme the roller lever.
Hierbei kann die Verriegelungsrichtung gemäß einer zweiten Variante ferner so ausgeführt sein, dass der Schaltbolzen in einem nicht mit dem vorbestimmten Druck beaufschlagten Zustand durch die Bolzenfeder in der zweiten Stellung (Verriegelungsstellung) gehalten wird, so dass Rollenhebel und Kipphebel miteinander drehfest verriegelt sind und in einem mit dem vorbestimmten Druck beaufschlagten Zustand in die erste Stellung gedrückt werden, in der der Schaltbolzen in den Kipphebel versenkt wird und die beiden Hebel voneinander entriegelt.In this case, the locking direction can be further designed according to a second variant, that the switching pin is held in a state not acted upon by the predetermined pressure by the bolt spring in the second position (locking position), so that roller lever and rocker arms are locked together rotatably and in one pressed state with the predetermined pressure are pressed into the first position in which the shift pin is sunk into the rocker arm and the two levers are unlocked from each other.
Die Gleitführungsaufnahme des Rollenhebels ist offen gestaltet, so dass die durch das Herausfahren des Schaltbolzens komprimierte Luft entweichen kann und keinen Widerstand gegen die Ausfahrbewegung des Schaltbolzens ausübt. Diese Öffnung ist bereits im Rohteil des Rollenhebels vorgesehen, so dass keine zusätzliche Entlüftungsbohrung benötigt wird.The Gleitführungsaufnahme the roller lever is designed to be open, so that the compressed by the retraction of the shift pin compressed air can escape and does not resist the extension movement of the shift pin. This opening is already provided in the blank of the roller lever, so that no additional vent hole is needed.
Der Kipphebel kann an seiner Unterseite, d. h. der dem Zylinderkopf zugewandten Seite, eine Geometrie zur axialen Fixierung auf einem Lagerbock aufweisen. Beispielsweise kann der Kipphebel eine Lagerung zur Befestigung an einem Kipphebellagerbock aufweisen, an dem die Kipphebelachse angeordnet ist, auf die der Kipphebel mit einer zugeordneten Bohrung schwenkbar aufgesteckt und mittels einer axialen Lagesicherung gehalten ist, wobei die axiale Lagesicherung eine Führungsverbindung als Eingriffselement-Gegenelement-Verbindung zwischen dem Lagerbock und dem Kipphebel ist, bei der ein quer zur Achsrichtung ausgerichtetes Eingriffselement, z. B. in Form eines Ringsteges, in ein zugeordnetes Gegenelement mit axialer Flankenabstützung schwenkbeweglich eingreift.The rocker arm can on its underside, d. H. the cylinder head facing side, have a geometry for axial fixation on a bearing block. For example, the rocker arm may have a mounting for attachment to a Kipphebellagerbock on which the rocker shaft is arranged, on which the rocker arm with an associated bore is pivotally mounted and held by an axial position assurance, wherein the axial position securing a guide connection as an engagement element counter-element connection between the bearing block and the rocker arm, in which a transversely aligned to the axial direction engagement element, for. B. in the form of an annular web, engages pivotally in an associated counter element with axial flank support.
Ein weiterer Aspekt der Erfindung betrifft ein Kraftfahrzeug, insbesondere ein Nutzfahrzeug, mit einem variablen Ventiltrieb, wie in diesem Dokument beschrieben.Another aspect of the invention relates to a motor vehicle, in particular a commercial vehicle, with a variable valve train, as described in this document.
Die zuvor beschriebenen bevorzugten Ausführungsformen und Merkmale der Erfindung sind beliebig miteinander kombinierbar. Weitere Einzelheiten und Vorteile der Erfindung werden im Folgenden unter Bezug auf die beigefügten Zeichnungen beschrieben. Es zeigen:
Figur 1- eine perspektivische Vorderansicht eines Ventiltriebs gemäß einer Ausführungs-form der Erfindung;
Figur 2- eine perspektivische Seitenansicht eines Ventiltriebs gemäß einer Ausführungs-form der Erfindung;
Figur 3- eine perspektivische Unteransicht eines Ventiltriebs gemäß einer Ausführungs-form der Erfindung;
Figur 4- eine Seitenansicht eines Kipphebels gemäß einer Ausführungsform der Erfindung; und
Figur 5- einen Schnitt
A-A durch Figur 4 .
- FIG. 1
- a front perspective view of a valve train according to an embodiment of the invention;
- FIG. 2
- a side perspective view of a valve train according to an embodiment of the invention;
- FIG. 3
- a perspective bottom view of a valve train according to an embodiment of the invention;
- FIG. 4
- a side view of a rocker arm according to an embodiment of the invention; and
- FIG. 5
- a cut AA through
FIG. 4 ,
Gleiche Teile sind in den Figuren mit denselben Bezugszeichen versehen, so dass die in den Figuren gezeigten verschiedenen Ansichten des Ventiltriebs auch aus sich heraus verständlich sind.Identical parts are provided in the figures with the same reference numerals, so that the different views of the valve train shown in the figures are also self-explanatory.
Die
Die Nockenwelle 7 weist einen mittleren Nocken 3, in diesem Dokument auch als erster Nocken bezeichnet, auf und zwei in Längsrichtung der Nockenwelle 7 gesehen versetzt angeordnete weitere Nocken 4, 5. Diese Nocken 4, 5 sind in diesem Dokument auch jeweils als zweite Nocken bezeichnet. Die beiden Nocken 4, 5 sind beidseitig von dem mittleren Nocken und benachbart zu diesem angeordnet. Der mittlere Nocken 3 und die beiden zweiten Nocken 4, 5 sind in ihrer Nockenkontur unterschiedlich gestaltetet. Die zweiten Nocken 4, 5 weisen einen größeren Nockenhub als der mittlere Nocken 3 auf.The
Ferner kann sich die Phasenlage des mittleren Nockens 3 gegenüber den zweiten Nocken 4, 5 unterscheiden. Der erste Nocken kann je nach Anwendung auch als Nullnocken ausgeführt sein, sodass die Ventile geschlossen bleiben.Furthermore, the phase angle of the
Von den beiden Nockenkonturen ist in einem Schaltzustand immer nur eine maßgeblich für die Ventilbewegung, was nachfolgend erläutert wird.Of the two cam contours in a switching state only one of the decisive for the valve movement, which will be explained below.
Der Ventiltrieb umfasst ferner eine Kipphebelanordnung, aufweisend einen um eine Kipphebelachse 2 verschwenkbar gelagerten Kipphebel 10, der an seinem nockenwellenseitigen Ende 11 über eine Druckrolle 13 des ersten Nockens 3 zugeordnet ist, um diese abzugreifen, und an seinem ventilseitigen Ende 12 in Wirkverbindung mit mindestens einem Hubventil steht.The valve train further comprises a rocker arm assembly comprising a
Der Kipphebel 10 ist an einem Kipphebellagerbock (nicht gezeigt) gehaltert, wobei an dem Kipphebellagerbock die Kipphebelachse 2 angeordnet ist, auf die der Kipphebel 10 mit einer zugeordneten Bohrung schwenkbar aufgesteckt und mittels einer axialen Lagesicherung gehalten ist.The
Die axiale Lagesicherung kann beispielsweise in an sich bekannter Weise über Anlageflächen an den Kipphebelflanken erfolgen. Diese Flanken können beispielsweise durch Kalibrierung des Schmiederohlings bzw. durch mechanische Bearbeitung erstellt sein. Lagerbockseitig kann die Fixierung ebenfalls über entsprechend bearbeitete Flächen sowie mittels Scheiben und Sicherungsringen erfolgen. Weiter sind axiale Lagesicherungen zwischen einem Kipphebel und der Achse bekannt. Beispielsweise weist dazu ein Bereich der Achse, welcher von der Bohrung des Kipphebels umschlossen ist, eine Ringnut auf, in der ein Sprengring verläuft, welcher zugleich mit seinem außen liegenden Ringabschnitt in einer Ringnut des Kipphebels verläuftThe axial position assurance can be done for example in a conventional manner via contact surfaces on the Kipphebelflanken. These flanks can be created for example by calibration of the forging blank or by mechanical processing. Bearing side, the fixation can also be done on appropriately machined surfaces and by means of washers and retaining rings. Next axial position locks between a rocker arm and the axle are known. For example, has an area of the axis, which is enclosed by the bore of the rocker arm, an annular groove in which a snap ring extends, which runs at the same time with its outer ring portion in an annular groove of the rocker arm
Im vorliegenden Ausführungsbeispiel ist die axiale Lagesicherung als Eingriffselement-Gegenelement-Verbindung zwischen dem Lagerbock und dem Kipphebel ausgeführt, bei der ein quer zur Achsrichtung ausgerichtetes Eingriffselement, z. B. in Form eines Ringsteges 16, in ein zugeordnetes Gegenelement (nicht dargestellt) mit axialer Flankenabstützung schwenkbeweglich eingreift.In the present embodiment, the axial position assurance is designed as an engagement element counter-element connection between the bearing block and the rocker arm, wherein a transversely aligned to the axial direction engagement element, for. B. in the form of an
Der ventilseitige Hebelarm 12 des Kipphebels 10 ist als Zwei-Ventil-Hebelarm ausgeführt, um zwei Ladungswechselventile gleichzeitig zu betätigen. Hierzu ist der ventilseitige Hebelarm 12 gabelförmig ausgeführt. An jedem ventilseitigen Ende des Hebelarms 12 ist eine Aufnahme 15 angeordnet. Die Aufnahme 15 kann zur Lagerung eines an sich bekannten hydraulischen Ventilspielausgleichelements (nicht dargestellt) verwendet werden. Anstatt eines hydraulischen Ventilspielausgleichselements kann in der Aufnahme 15 auch eine Schraube mit Elefantenfuß aufgenommen sein, mittels derer ein Ventilspiel manuell nachjustiert werden kann.The valve-
Hydraulische Ventilspielausgleichselemente (HVA) in Brennkraftmaschinen sind an sich bekannt und dienen dazu, insbesondere die sich über die Betriebsdauer ändernden Längenabmessungen der Ladungswechselventile so auszugleichen, dass in der Grundkreisphase des das Ventil betätigenden Nockens ein sicheres Ventilschließen gewährleistet ist. Dabei soll andererseits die Nockenerhebung verlustfrei auf das Ventil übertragen und somit in eine Ventilhubbewegung umgewandelt werden. Die Wirkungsweise derartiger hydraulischer Ventilspielausgleichselemente, die im Kraftfluss einer Ventilsteuerung, insbesondere einer Brennkraftmaschine, angeordnet sind, wird als bekannt vorausgesetzt.Hydraulic valve clearance compensation elements (HVA) in internal combustion engines are known per se and serve, in particular, to compensate for the change over the operating length length dimensions of the charge exchange valves so that in the base circle phase of the valve-actuating cam secure valve closing is ensured. On the other hand, the cam lobe should be transferred without loss to the valve and thus converted into a valve lift. The operation of such hydraulic valve clearance compensation elements, which are arranged in the power flow of a valve control, in particular an internal combustion engine, is assumed to be known.
Zur Ausbildung eines variablen Ventiltriebs umfasst der Ventiltrieb 1 ferner einen Rollenhebel 20, der an seinem nockenwellenseitigen Ende 21 den beiden zweiten Nocken 4, 5 zugeordnet ist und an seinem anderen Ende am Kipphebel 10 um die Kipphebelachse 2 verschwenkbar angelenkt ist.To form a variable valve train, the
Der Kipphebel 10 ist über einen Gelenkstift 25 drehbar mit dem Rollenhebel 20 verbunden. Für diese Verbindung befindet sich am Kipphebel 10 eine Gelenkstiftaufnahme 14 sowie am Rollenhebel 20 eine Gelenkstiftaufnahme 24. Die zueinander fluchtenden Gelenkstiftaufnahmen 14, 24 sind an einer oberen Seite, d. h. einer dem Zylinderkopf abgewandten Seite, des Kipphebels 10 angeordnet, und zwar an einem mittleren Bereich des Kipphebels 10, welcher die zylindrische Ausnehmung des Kipphebels ausbildet, in der die Kipphebelachse 2 aufgenommen ist.The
Der nockenwellenseitige Hebelarm 11 des Kipphebels 10 führt an seinem Ende eine Druckrolle 13, die dem mittleren Nocken 3 zugeordnet ist, um den Nocken 3 bzw. deren Drehbewegung abzugreifen.The camshaft
Der Rollenhebel weist zwei sich zur Nockenwelle / hin erstreckende, parallele Arme 21 auf, die sich jeweils auch - in Längsrichtung der Nockenwelle / gesehen - auf unterschiedlichen Seiten vom nockenwellenseitigen Hebelarm 11 des Kipphebels 10 erstrecken.The roller lever has two to the camshaft / down extending,
Jeder der beiden Arme 21 führt am Ende ebenfalls eine Druckrolle 23. Jeder der Druckrollen 23 ist einer der beiden zweiten Nocken 4, 5 zugeordnet, um diese abzugreifen.Each of the two
Sowohl der Kipphebel 10 als auch der Rollenhebel 20 sind somit zur Kipphebelachse 2 drehbar gelagert und unabhängig voneinander zur Kipphebelachse verschwenkbar - zumindest dann, wenn Kipphebel 10 und Rollenhebel 20 nicht miteinander durch die schaltbare hydraulische Verriegelungseinrichtung verriegelt sind.Both the
Der Kipphebel 10 und der Rollenhebel 20 sind ferner über zwei beidseitig befestigte Rückstellfedern 6 miteinander verspannt, so dass der Rollenhebel 20 permanent an den Kipphebel 10 gedrückt wird, während die Nockenwelle / sich in einer Grundkreisstellung befindet. Unter einer Grundkreisphase bzw. Nockengrundkreisphase soll dabei insbesondere ein Winkelbereich der Nockeneinheit verstanden werden, in dem Nockenkonturen sämtlicher Teilnocken der Nockeneinheit ein gemeinsames Grundkreisniveau einnehmen.The
Diese Rückstellfedern 6 drücken auf die Anlagestelle 17 des Kipphebels 10 (siehe
Der variable Ventiltrieb 1 umfasst ferner eine schaltbare hydraulische Verriegelungseinrichtung bzw. ein hydraulisches Schaltelement 30, durch die bei Zuschaltung der Kipphebel 10 und der Rollenhebel 20 starr miteinander verriegelt werden und beide der Bewegung der zweiten Nocken 4, 5 folgen.The
Im Kipphebel 10 befindet sich hierzu die schaltbare hydraulische Verriegelungseinrichtung 30, deren Aufbau anhand der
Die schaltbare hydraulische Verriegelungseinrichtung 30 umfasst einen Führungsbolzen 34, auf den eine Bolzenfeder 33 aufgesteckt ist. Der Führungsbolzen 34 und die Bolzenfeder 33 befinden sich in einer Gleitführungsbohrung 37, die in den nockenwellenseitigen Hebelarm 11 des Kipphebels 10 eingebracht ist. In der Gleitführungsbohrung 37 ist der Führungsbolzen 34 mit einem Schaltbolzen 31 verschraubt. Die Bolzenfeder 34 kommt an einem Federanschlag 32 zur Anlage. Der Schaltbolzen 31 weist außerdem eine Nullpunktanlage 36 auf. In einem Grundzustand (keine Druckbeaufschlagung) wird der Schaltbolzen 31 von der Bolzenfeder 33 an die Nullpunktanlage 36 gedrückt. Hinter dem Schaltbolzen 31 befindet sich eine Druckkammer 35, welche zur Betätigung der Schaltung mit Öl gefüllt wird. Durch den Öldruck in der Druckkammer 35 wird der Schaltbolzen 31 mit dem verschraubten Führungsbolzen 34 herausgedrückt, so dass die Bolzenfeder 33 gestaucht wird. Dabei kommt der Führungsbolzen 34 auf der Anlagefläche 38 zum Anschlag, so dass eine definierte Endlage im ausgefahrenen Zustand der beiden Bolzen 31, 34 gegeben ist.The switchable
In diesem ausgefahrenen Zustand des Schaltbolzens 31 ragt dieser aus dem Kipphebelarm 11 heraus - in Richtung eines benachbarten Arms 21 des Rollenhebels 10 - und greift in eine fluchtend vorgesehene Gleitführungsaufnahme (nicht dargestellt) des Rollenhebels 10 ein. Dadurch verriegelt der Schaltbolzen 31 im ausgefahrenen Zustand den Kipphebel 10 mit dem Rollenhebel. In diesem Zustand sind Kipphebel 10 und Rollenhebel 20 nicht mehr unabhängig voneinander um die Kipphebelachse 2 verschwenkbar, sondern nur noch gemeinsam. In diesem verriegelten Zustand folgen der Kipphebel 10 und der Rollenhebel 20 der Nockenkontur der zweiten Nocken 4, 5, da diese den größeren Hub aufweisen.In this extended state of the
Lässt der Öldruck nach, wird der Schaltbolzen 31 samt Führungsbolzen 34 durch die Federkraft der Bolzenfeder 33 wieder gegen die Nullpunktanlage 36 gedrückt, und der Rollenhebel 20 wird wieder vom Kipphebel 10 entkoppelt.Lets the oil pressure, the
Kipphebel 10 und Rollenhebel 20 sind somit bei nicht zugeschalter hydraulischer Verriegelungsrichtung 30 unabhängig voneinander um die Kipphebelachse 2 drehbar gelagert, so dass die zweiten Nocken 4, 5 unwirksam sind, d. h., die zweiten Nocken 4, 5 betätigen zwar den Rollenhebel 20, der aber nur Kippbewegungen ausführt, ohne Einflussnahme auf das Ventil. Dagegen sind bei zugeschalter Verriegelungsrichtung Kipphebel und Rollenhebel drehfest miteinander verbunden, so dass beide nur gemeinsam um die Kipphebelachse 2 verschwenkbar sind.
Durch wahlweise Beaufschlagung der Druckkammer 35 mit einem hydraulischen Druck kann somit zu einem gewünschten Zeitpunkt, z. B. in Abhängigkeit von Betriebsparametern, von der ersten Nockenkontur des mittleren Nockens 3 auf eine alternative Nockenkontur der zweiten Nocken 4, 5 umgeschaltet werden und umgekehrt, um die Gaswechselventile der Brennkraftmaschine variabel mit unterschiedlichen Öffnungs- und Schließzeitpunkten und/oder mit unterschiedlichen Ventilöffnungshüben zu betreiben.By selectively pressurizing the
- 11
- Ventiltriebvalve train
- 22
- Kipphebelachserocker shaft
- 33
- Erster Nocken, z. B. mittlerer NockenFirst cam, z. B. middle cam
- 4, 54, 5
- Zweite NockeSecond cam
- 66
- RückstellfederReturn spring
- 77
- Nockenwellecamshaft
- 1010
- Kipphebelrocker arm
- 1111
- Nockenwellseitiger HebelarmCamshaft side lever arm
- 1212
- Ventilseitiger HebelarmValve side lever arm
- 13, 2313, 23
- Druckrollepressure roller
- 14, 2414, 24
- GelenkstiftaufnahmeWrist pin receiving
- 1515
- Aufnahmeadmission
- 1616
- Ringstegring land
- 17, 2717, 27
- Anlegestelle für RückstellfederMooring for return spring
- 2020
- Rollenhebelroller lever
- 21, 2221, 22
- Hebelarmlever arm
- 2323
- Anlegestelle für RückstellfederMooring for return spring
- 2525
- Gelenkstiftpintle
- 3030
- Hydraulische VerriegelungseinrichtungHydraulic locking device
- 3131
- Schaltbolzenswitching pin
- 3232
- Federanschlagspring stop
- 3333
- Bolzenfederpin spring
- 3434
- Führungsbolzenguide pins
- 3535
- Druckkammerpressure chamber
- 3636
- NullpunktanlageZero conditioning
- 3737
- GleitführungsbohrungGleitführungsbohrung
- 3838
- Anlageflächecontact surface
Claims (10)
- Variable valve train (1) for a lifting valve, in particular for a gas exchange valve of an internal combustion engine, which valve can be moved periodically indirectly by way of a cam via a rocker arm between a closed and an open position, comprising(a) a camshaft (7), having at least one first cam (3) and at least one second cam (4, 5) which is arranged offset in the longitudinal direction of the camshaft (7), the at least one first cam (3) and the at least one second cam (4, 5) being of different design in terms of their cam contour;(b) a rocker arm (10) which is mounted such that it can be pivoted about a rocker arm axis (2), which rocker arm (10) is assigned to the at least one first cam (3) via a roller (13) at its camshaft-side end (11) and is operatively connected to at least one lifting valve at its valve-side end (12);(c) a roller lever (20) which is assigned to the at least one second cam (4, 5) via at least one roller (23) at its camshaft-side end (21) and is articulated at its other end on the rocker arm (10) such that it can be pivoted about the rocker arm axis (2),(d) a switchable hydraulic locking device (30), by way of which the rocker arm (10) and the roller lever (20) can optionallycharacterized(d1) be locked rigidly to one another, both following the movement of the at least one second cam (4, 5), or(d2) be unlocked from one another, both following the respectively associated cams (3, 4, 5) independently of one another,(a) in that the roller lever (20) is connected to the rocker arm (10) via a hinge (14, 24, 25); and/or(b) in that the rocker arm (10) and the roller lever (20) in each case have a pivot pin seat (14, 24), which pivot pin seats (14, 24) are aligned with respect to one another and have an inserted pivot pin (25).
- Variable valve train (1) according to Claim 1, characterized in that(a) in each case one second cam (4, 5) is provided on both sides of the first cam (3), and the roller lever (20) extends on both sides from the camshaft-side end (11) of the rocker arm (10) and follows the cam contour of the two second cams (4, 5), or(b) in each case one first cam (3) is provided on both sides of the second cam (4, 5), and the camshaft-side end of the rocker arm (10) extends on both sides from the roller lever (20) and follows the cam contour of the two first cams (3).
- Variable valve train (1) according to one of the preceding claims, characterized in that the rocker arm (10) and the roller lever (20) are braced against one another via at least one restoring spring (6) in such a way that the rollers (13; 23) of the rocker arm (10) and the roller lever (20) are aligned with respect to one another in a base circle position.
- Variable valve train (1) according to Claim 3, characterized in that two restoring springs (6) of this type are provided which are arranged on different sides of the rocker arm (10) as viewed in the longitudinal direction of the rocker arm axis (2).
- Variable valve train (1) according to one of the preceding claims, characterized in that the switchable hydraulic locking device (30) comprises a hydraulically actuable switching pin (31) which can be moved from a first position into a second position by way of loading with a predefined hydraulic pressure, the switching pin (31) permitting a relative movement of the rocker arm (10) and the roller lever (20) with respect to one another in the first position, and preventing a relative movement of the rocker arm (10) and the roller lever (20) about the rocker arm axis (2) in the second position.
- Variable valve train according to Claim 5, characterized in that a guide pin (34), a pin spring (33) which is plugged onto the guide pin (34), and the switching pin (31) which is screwed to the guide pin (34) are arranged in the rocker arm (10) in a sliding guide bore (37), and the switching pin (31) can be loaded with a predefined oil pressure via a pressure chamber (18) which can be filled with oil in order to actuate the switching means, the locking device (30) being configured in such a way that the switching pin (31), in a state in which it is not loaded with the predefined pressure, is held by way of the pin spring (33) which acts as a restoring spring and the guide pin (34)(a) in the first position, and that the switching pin (31), in a state in which it is loaded with the predefined pressure, is pressed into the second position, in which the switching pin (31) protrudes out of the rocker arm (10) in the direction of the roller lever (20) and moves into an aligned sliding guide seat of the roller lever (20), or(b) is held in the second position, and that the switching pin (31), in a state in which it is loaded with the predefined pressure, is pressed into the first position, in which the rocker arm (10) moves in, with the result that it releases the aligned sliding guide seat of the roller lever (20).
- Variable valve train according to one of the preceding claims, characterized in that the cam contour of the at least one first cam (3) has a different cam elevation and/or a different phase position in comparison with the cam contour of the at least one second cam (4, 5).
- Variable valve train according to one of the preceding claims, characterized in that, at its valve-side end (12), the rocker arm (10) has a seat (15), in which a hydraulic valve play compensating element or a screw with an elephant foot formation is received.
- Variable valve train according to one of the preceding claims, characterized by a bearing system of the rocker arm (10), having a rocker arm bearing block, on which the rocker arm axis is arranged, onto which the rocker arm is plugged pivotably by way of an associated bore and is held by means of an axial positional securing means, the axial positional securing means being a guide connection as engagement element/counterelement connection between the bearing block and the rocker arm, in which an engagement element (16) which is oriented transversely with respect to the axial direction engages into an associated counterelement with axial flank support in a pivotably movable manner.
- Motor vehicle, in particular commercial vehicle, having a valve train (1) according to one of the preceding claims.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102015015087.1A DE102015015087A1 (en) | 2015-11-20 | 2015-11-20 | Variable valve train with a rocker arm |
Publications (2)
Publication Number | Publication Date |
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EP3170997A1 EP3170997A1 (en) | 2017-05-24 |
EP3170997B1 true EP3170997B1 (en) | 2019-10-16 |
Family
ID=57211234
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP16002314.9A Active EP3170997B1 (en) | 2015-11-20 | 2016-10-28 | Variable valve drive with a rocker arm |
Country Status (6)
Country | Link |
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US (1) | US10400639B2 (en) |
EP (1) | EP3170997B1 (en) |
CN (1) | CN107035451B (en) |
BR (1) | BR102016026679B1 (en) |
DE (1) | DE102015015087A1 (en) |
RU (1) | RU2723650C2 (en) |
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CN111315967B (en) * | 2017-11-10 | 2022-05-31 | 伊顿智能动力有限公司 | Additional motion double lift rocker arm |
DE102017129720A1 (en) | 2017-12-13 | 2019-06-13 | Schaeffler Technologies AG & Co. KG | Switchable rocker arm assembly |
DE102017129719A1 (en) | 2017-12-13 | 2019-06-13 | Schaeffler Technologies AG & Co. KG | Switchable rocker arm assembly |
DE102018207459A1 (en) * | 2018-05-15 | 2019-11-21 | Mahle International Gmbh | Valve drive device |
CN112513430B (en) * | 2018-07-27 | 2023-01-20 | 伊顿智能动力有限公司 | Center pivot latch deactivation rocker arm |
CN112585337B (en) | 2018-08-09 | 2023-03-28 | 伊顿智能动力有限公司 | Deactivating rocker arm with two-step latch pin |
US11566544B2 (en) | 2018-08-09 | 2023-01-31 | Eaton Intelligent Power Limited | Rocker arm assembly with lost motion spring |
KR102546519B1 (en) * | 2018-12-07 | 2023-06-21 | 자콥스 비히클 시스템즈, 인코포레이티드. | A valve actuation system comprising two rocker arms and a collapsing mechanism |
US11486274B2 (en) | 2018-12-07 | 2022-11-01 | Jacobs Vehicle Systems, Inc. | Valve actuation system comprising at least two rocker arms and a one-way coupling mechanism |
DE102018132857A1 (en) | 2018-12-19 | 2020-06-25 | Man Truck & Bus Se | Switchable actuating device for a lift valve of an internal combustion engine, internal combustion engine and motor vehicle |
CN110109567B (en) | 2019-04-24 | 2020-07-10 | 武汉华星光电半导体显示技术有限公司 | Touch pad, touch display and manufacturing method of touch pad |
EP3935271A4 (en) * | 2019-05-10 | 2022-12-14 | Cummins, Inc. | Valve train system for extended duration intake valve opening |
WO2021143995A1 (en) * | 2020-01-17 | 2021-07-22 | Eaton Intelligent Power Limited | Electromagnetic latch systems for rocker arm assemblies |
WO2021164950A1 (en) * | 2020-02-19 | 2021-08-26 | Eaton Intelligent Power Limited | Rocker arm assembly, compliance capsules, actuators, and support structures |
CN112360586A (en) * | 2020-11-10 | 2021-02-12 | 蔡金洲 | Automobile gas distribution machine mechanism accessory |
DE112022002610T5 (en) * | 2021-07-23 | 2024-03-14 | Eaton Intelligent Power Limited | ROCKER ARRANGEMENT WITH MAIN ROCKER ARM AND FORKED AUXILIARY ROCKER ARM |
DE102021126256A1 (en) | 2021-10-11 | 2023-04-13 | Schaeffler Technologies AG & Co. KG | Carrier module for a switchable valve train of a heavy-duty internal combustion engine |
WO2024002523A1 (en) * | 2022-06-29 | 2024-01-04 | Eaton Intelligent Power Limited | Rocker system with stopper arrangement on cam side |
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- 2015-11-20 DE DE102015015087.1A patent/DE102015015087A1/en not_active Withdrawn
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2016
- 2016-10-28 EP EP16002314.9A patent/EP3170997B1/en active Active
- 2016-11-14 BR BR102016026679-3A patent/BR102016026679B1/en active IP Right Grant
- 2016-11-18 CN CN201611015615.7A patent/CN107035451B/en active Active
- 2016-11-18 US US15/355,573 patent/US10400639B2/en active Active
- 2016-11-18 RU RU2016145153A patent/RU2723650C2/en active
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JP2006132378A (en) * | 2004-11-04 | 2006-05-25 | Otics Corp | Variable valve system |
Also Published As
Publication number | Publication date |
---|---|
CN107035451B (en) | 2020-09-04 |
RU2016145153A (en) | 2018-05-18 |
CN107035451A (en) | 2017-08-11 |
US10400639B2 (en) | 2019-09-03 |
DE102015015087A1 (en) | 2017-05-24 |
EP3170997A1 (en) | 2017-05-24 |
BR102016026679B1 (en) | 2022-10-04 |
BR102016026679A2 (en) | 2018-06-05 |
RU2723650C2 (en) | 2020-06-17 |
US20170145876A1 (en) | 2017-05-25 |
RU2016145153A3 (en) | 2020-02-12 |
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