EP3014080B1 - Spring arrangement for a variable valve drive of an internal combustion engine - Google Patents
Spring arrangement for a variable valve drive of an internal combustion engine Download PDFInfo
- Publication number
- EP3014080B1 EP3014080B1 EP14715302.7A EP14715302A EP3014080B1 EP 3014080 B1 EP3014080 B1 EP 3014080B1 EP 14715302 A EP14715302 A EP 14715302A EP 3014080 B1 EP3014080 B1 EP 3014080B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- camshaft
- intermediate lever
- spring
- variable valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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- 238000002485 combustion reaction Methods 0.000 title claims description 14
- 238000009434 installation Methods 0.000 description 5
- 230000001419 dependent effect Effects 0.000 description 1
- 239000000446 fuel Substances 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
- 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
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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
- F01L1/14—Tappets; Push rods
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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
- F01L13/0021—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 by modification of rocker arm ratio
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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
- F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
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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
- F01L1/185—Overhead end-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
- 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
- F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
- F01L2013/0068—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
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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
Definitions
- the invention relates to a spring arrangement for a variable valve train of an internal combustion engine with an intermediate lever, at least one camshaft roller on the intermediate lever, which rests against a camshaft, a link roller on the intermediate lever, which abuts against a link, at least one control shaft roller on the intermediate lever, which rests against a control shaft and is arranged on the side facing away from the backdrop of the camshaft pulley, at least one working cam contour which is formed at the opposite end of the intermediate lever to the camshaft and acts on a roller cam follower of a gas exchange valve and at least one spring element, via which the camshaft roller of the intermediate lever against the camshaft and the Sliding roller is loaded against the backdrop.
- Variable valve trains have become known in recent years for reducing fuel demand and emissions in various designs.
- the roller drag of the gas exchange valves is no longer actuated directly via the camshaft but via a working cam contour of an intermediate lever.
- this intermediate lever Upon rotation of the camshaft, this intermediate lever is guided over a first roller on a contour, so that this tilting movement of the intermediate lever has a movement of the working cam contour on the role of Rollenschlepphebels result.
- how the working curve acts on this roller rocker arm is dependent on the position of a rotatable control shaft which acts on a second roller of the intermediate lever.
- spring elements are used, which are usually designed as double torsion springs with two oppositely wound helices and their two spring legs each biased against one of the cam follower, while the intermediate leg is clamped, for example, on the component forming the link.
- a secondary spring biased biased in height of the axis of the control shaft roller against the intermediate lever and so press the roller against the control shaft is in the DE 10 2007 047 582 A1 on the backdrop component and in the DE 10 2004 003 327 A1 attached to the control shaft.
- an end leg of the spring element biased against the working cam contour and the camshaft side of the intermediate lever abuts against a contact surface of the intermediate lever and the spring element on the contact surface has a force component in the direction of the camshaft and in the direction of the backdrop, wherein the contact surface on the to the working curve contour opposite side of a rotation axis of the camshaft roller is arranged on the intermediate lever, so that the spring element generates a torque about the axis of rotation of the camshaft pulley of the intermediate lever, a secure contact of the intermediate lever is made to the camshaft and the scenery.
- the bearing clearances and tolerances of the intermediate lever are compensated and distributes the forces acting on the waves particularly advantageous.
- the intermediate lever Due to the generated torque, the intermediate lever also enters into a fixed abutment with the control shaft, but without these being subjected to an excessive contact pressure. Accordingly, a sufficient contact force is produced by means of a single spring element for all contact points of the intermediate lever.
- the spring element is a double leg spring, whose intermediate leg is attached to the bearing housing of the variable valve drive and whose end legs bear against each biased a projection forming the projection of two juxtaposed intermediate lever members of the intermediate lever.
- the helix of the spring element is arranged on the side facing away from the camshaft and the roller rocker arm side of the intermediate lever.
- the spring element is easy to install and, if necessary, to change due to the good accessibility.
- the helix of the spring element on the side facing the roller rocker arm is the Camshaft arranged, whereby the required space is reduced.
- the helix is arranged in the region of an axial extension of a rotation axis of a roller of the roller cam follower.
- the desired forces and torques can be introduced in a suitable manner and on the other hand, the spring element can be integrated in a compact manner in the variable valve train.
- the two juxtaposed Rollenschlepphebel which are associated with a double leg spring between the two helices of the double leg spring are arranged so that a good accessibility of the spring element is maintained.
- the two helices of the double leg spring between the two juxtaposed Rollenschlepphebeln which are associated with a double leg spring arranged, whereby the spring leg lengths can be formed shortened.
- a spring arrangement for a variable valve train of an internal combustion engine with which the required contact forces are produced by means of only one spring element in all three desired contact points and, in addition, no excessive forces are exerted on bearings or rollers.
- the intermediate lever is reliably positioned, its bearing clearances compensated and created a tolerance compensation. There is a low installation effort and space requirements.
- variable valve train shown in the figures consists of a camshaft 10 which is operatively connected via an intermediate lever 12 to a roller cam follower 14, which in turn has a connection to a valve rod 16 of a gas exchange valve 18 serving as an inlet valve.
- it is an internal combustion engine with two intake valves per cylinder, each associated with a roller cam followers 14.
- the intermediate lever 12 In order to transmit the actuating force of the camshaft 10 to the gas exchange valve 18, the intermediate lever 12 must be positioned and guided. For a completely defined, guided tilting movement for actuating a gas exchange valve 18, the intermediate lever 12 must have three contact points. In the present exemplary embodiment, there are a total of five contact points, since two gas exchange valves 18 are to be actuated via the one intermediate lever 12, which has two intermediate lever members 20 for this purpose, which have a common axis of rotation 22 are connected to each other, on the inside of the two intermediate lever members 20 each have a camshaft roller 24 is arranged and on the between the two intermediate lever members 20 a link roller 26 which bears against a gate 28 which is fixed to the bearing housing, not shown.
- the other two contact points consist between a control shaft 30 and two control shaft rollers 32, one of which is arranged in the interior of an intermediate lever member 20 each.
- the two control shaft rollers 32 are mounted in the intermediate lever members 20 and are located between the camshaft pulley 24 of the respective intermediate lever member 20 and an opposite to the camshaft pulley 24 end of the intermediate lever member 20 working cam contour 34 which abuts against a cam follower roller 36 of the roller cam follower 14.
- a spring element 44 is used in the form of a double leg spring according to the invention.
- This has two oppositely wound helices 46, which are connected to each other via an intermediate leg 48 with a U-shaped inversion.
- the spring element 44 has end legs 50.
- this spring element 44 is arranged and formed such that its intermediate leg 48 is fastened in a bearing housing fixedly arranged intermediate leg receptacle 52, which is arranged between the two intermediate lever members 20, the link 28 and the roller cam followers 14. From here, the wires of the spring element extend in opposite axial directions to the respective side of the roller rocker arm 14 opposite to the intermediate leg receiver 52. Approximately in extension of the axis 35 of the rocker arm rollers 36, the respective helix 46 of the spring element is formed outside the intermediate lever 12.
- helices 46 each extend the end leg 50 of the spring element 44 approximately in the extension direction of the intermediate lever members 20 and that to the end of the intermediate lever members 20 beyond the axis 22 of the camshaft rollers 24, where in each case a projection 54 is formed, which a contact surface 56, against which a bent end 58 of the end leg 50 is biased in the direction of the camshaft 10.
- the projection 54 is to be arranged on the intermediate lever 12 such that a component of the spring force points in the direction of the link 28.
- this pressing force by the spring element 44 also creates a torque about the axis of rotation 22 of the camshaft pulley 24 and the intermediate lever 12, which causes the control shaft roller 32 is pressed against the control shaft 30.
- the spring element 44 produces a defined position of the intermediate lever 12 via the three or five support points on the intermediate lever 12.
- the already loaded by high forces during operation control shaft roller 32 and control shaft 30 is not burdened by excessive forces, as would be the case if the force would be introduced from the opposite side of the intermediate lever 12.
- FIG. 2 A substantially same-acting embodiment is in the FIG. 2 represented, wherein the same components are provided with the same reference numerals.
- the only significant difference between the two embodiments is the arrangement of the spring element 44th
- This spring element 44 has in comparison to the first embodiment, two helices 46, which are directly axially adjacent to each other, so that the axis of the helices 46 as well as the intermediate leg 48 between the link 28, the camshaft 10, the two intermediate lever members 20 and the Rollenschlepphebeln fourteenth is arranged and is located on the opposite to the control shaft 30 side of the intermediate lever 12.
- the end legs 50 have between the two intermediate lever members 20 past them and biased behind a projection 54, which on the camshaft 10 and substantially also to working cam contour 34 opposite side of the respective intermediate lever member 20.
- This projection 54 is arranged so that resulting force vector has a component which points in the direction of the camshaft 10 and has a component which points in the direction of the guide 28.
- a torque is generated about the axis 22, by which a contact force between the control shaft roller 32 and the control shaft 30 is formed.
- this spring element is somewhat more expensive to assemble, it requires less installation space.
- a secure system of the intermediate lever is ensured in the required support points with only one spring element. The contact forces are distributed so that no overloading of the rollers or bearings is to be feared. The installation effort and the required installation space are minimized.
- the two helices can also be arranged above the gate on the opposite side to the camshaft and engage behind the corresponding projection on the one hand to generate the contact force against the camshaft and the link and on the other hand the torque about the camshaft axis, through which the control shaft roller against the control shaft is charged.
- the spring assembly for differently constructed variable valve trains or engines are suitable, so that, for example, a different number of intake valves per cylinder is needed. Further modified arrangements are conceivable within the scope of the main claim.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
Die Erfindung betrifft eine Federanordnung für einen variablen Ventiltrieb einer Verbrennungskraftmaschine mit einem Zwischenhebel, zumindest einer Nockenwellenrolle am Zwischenhebel, die gegen eine Nockenwelle anliegt, einer Kulissenrolle am Zwischenhebel, die gegen eine Kulisse anliegt, zumindest einer Steuerwellenrolle am Zwischenhebel, die gegen eine Steuerwelle anliegt und an der zur Kulisse abgewandten Seite der Nockenwellenrolle angeordnet ist, zumindest einer Arbeitskurvenkontur, die an dem zur Nockenwellenrolle entgegen gesetzten Ende des Zwischenhebels ausgebildet ist und auf einen Rollenschlepphebel eines Gaswechselventils wirkt sowie zumindest einem Federelement, über welches die Nockenwellenrolle des Zwischenhebels gegen die Nockenwelle und die Kulissenrolle gegen die Kulisse belastet ist.The invention relates to a spring arrangement for a variable valve train of an internal combustion engine with an intermediate lever, at least one camshaft roller on the intermediate lever, which rests against a camshaft, a link roller on the intermediate lever, which abuts against a link, at least one control shaft roller on the intermediate lever, which rests against a control shaft and is arranged on the side facing away from the backdrop of the camshaft pulley, at least one working cam contour which is formed at the opposite end of the intermediate lever to the camshaft and acts on a roller cam follower of a gas exchange valve and at least one spring element, via which the camshaft roller of the intermediate lever against the camshaft and the Sliding roller is loaded against the backdrop.
Variable Ventiltriebe sind in den letzten Jahren zur Verminderung des Kraftstoffbedarfs und der Emissionen in verschiedenen Ausführungen bekannt geworden. Bei diesen variablen Ventiltrieben wird der Rollenschleppheble der Gaswechselventile nicht mehr direkt über die Nockenwelle betätigt, sondern über eine Arbeitskurvenkontur eines Zwischenhebels. Bei Drehung der Nockenwelle wird dieser Zwischenhebel über eine erste Rolle auf einer Kontur geführt, so dass diese Kippbewegung des Zwischenhebels eine Bewegung der Arbeitskurvenkontur auf der Rolle des Rollenschlepphebels zur Folge hat. Wie die Arbeitskurve auf diesen Rollenschlepphebel wirkt ist jedoch abhängig von der Stellung einer drehbaren Steuerwelle, die auf eine zweite Rolle des Zwischenhebels wirkt. Durch Änderung der Stellung der Steuerwelle entsteht eine geänderte Kippbewegung der Arbeitskurvenkontur und somit eine geänderte Öffnungs- und Schließbewegung des Gaswechselventils.Variable valve trains have become known in recent years for reducing fuel demand and emissions in various designs. In these variable valve trains, the roller drag of the gas exchange valves is no longer actuated directly via the camshaft but via a working cam contour of an intermediate lever. Upon rotation of the camshaft, this intermediate lever is guided over a first roller on a contour, so that this tilting movement of the intermediate lever has a movement of the working cam contour on the role of Rollenschlepphebels result. However, how the working curve acts on this roller rocker arm is dependent on the position of a rotatable control shaft which acts on a second roller of the intermediate lever. By changing the position of Control shaft creates a modified tilting movement of the working curve contour and thus a changed opening and closing movement of the gas exchange valve.
Um diese Funktionsweise mit ausreichender Genauigkeit ausführen zu können, ist es daher erforderlich, die Rollen des Zwischenhebels sowohl gegen die Kulisse als auch gegen die Nockenwelle und die Steuerwelle anzupressen, und zwar in allen Positionen der Nockenwelle der Kulisse und der Steuerwelle. Hierzu werden Federelemente verwendet, die zumeist als Doppelschenkelfedern mit zwei entgegengesetzt gewickelten Helices ausgebildet sind und deren zwei Federendschenkel jeweils vorgespannt gegen einen der Schlepphebel anliegen, während der Zwischenschenkel beispielsweise an dem die Kulisse bildenden Bauteil festgespannt ist.To perform this operation with sufficient accuracy, it is therefore necessary to press the rollers of the intermediate lever both against the backdrop and against the camshaft and the control shaft, in all positions of the camshaft of the gate and the control shaft. For this purpose, spring elements are used, which are usually designed as double torsion springs with two oppositely wound helices and their two spring legs each biased against one of the cam follower, while the intermediate leg is clamped, for example, on the component forming the link.
So wird in der
Diese Ausführung hat jedoch den Nachteil, dass zwei verschieden Federelemente verwendet werden müssen, um ausreichende Anpresskräfte zu erzeugen. Entsprechend wird in der
Es stellt sich daher die Aufgabe, eine Federanordnung für einen variablen Ventiltrieb einer Verbrennungskraftmaschine bereit zu stellen, mit der die notwendigen Kontaktkräfte der Anlagepunkte des Zwischenhebels sichergestellt werden, ohne dass zu hohe auftretende Querkräfte auf die Steuerwelle wirken. Dabei sollen der Montageaufwand und der Bauraumbedarf reduziert werden.It is therefore the object to provide a spring arrangement for a variable valve train of an internal combustion engine, with the necessary contact forces of the contact points of the intermediate lever can be ensured without excessive lateral forces acting on the control shaft. The installation effort and space requirements are to be reduced.
Diese Aufgabe wird durch eine Federanordnung für einen variablen Ventiltrieb mit den Merkmalen des Hauptanspruchs gelöst.This object is achieved by a spring arrangement for a variable valve train having the features of the main claim.
Dadurch, dass ein Endschenkel des Federelements an einer von der Arbeitskurvenkontur und der Nockenwelle abgewandten Seite des Zwischenhebels vorgespannt gegen eine Anlagefläche des Zwischenhebels anliegt und das Federelement an der Anlagefläche eine Kraftkomponente in Richtung der Nockenwelle und in Richtung der Kulisse aufweist, wobei die Anlagefläche auf der zur Arbeitskurvenkontur entgegengesetzten Seite einer Drehachse der Nockenwellenrolle am Zwischenhebel angeordnet ist, so dass das Federelement ein Drehmoment um die Drehachse der Nockenwellenrolle des Zwischenhebels erzeugt, wird eine sichere Anlage des Zwischenhebels an der Nockenwelle und der Kulisse hergestellt. Die Lagerspiele und Toleranzen des Zwischenhebels werden kompensiert und die auf die Wellen wirkenden Kräfte besonders vorteilhaft verteilt. Durch das erzeugte Drehmoment gelangt der Zwischenhebel auch in eine feste Anlage zur Steuerwelle, jedoch ohne dass diese mit einer zu großen Anpresskraft beaufschlagt würde. Entsprechend wird mittels eines einzelnen Federelementes für alle Anlagepunkte des Zwischenhebels eine ausreichende Kontaktkraft hergestellt.Characterized in that an end leg of the spring element biased against the working cam contour and the camshaft side of the intermediate lever abuts against a contact surface of the intermediate lever and the spring element on the contact surface has a force component in the direction of the camshaft and in the direction of the backdrop, wherein the contact surface on the to the working curve contour opposite side of a rotation axis of the camshaft roller is arranged on the intermediate lever, so that the spring element generates a torque about the axis of rotation of the camshaft pulley of the intermediate lever, a secure contact of the intermediate lever is made to the camshaft and the scenery. The bearing clearances and tolerances of the intermediate lever are compensated and distributes the forces acting on the waves particularly advantageous. Due to the generated torque, the intermediate lever also enters into a fixed abutment with the control shaft, but without these being subjected to an excessive contact pressure. Accordingly, a sufficient contact force is produced by means of a single spring element for all contact points of the intermediate lever.
In einer bevorzugten Ausführungsform ist das Federelement eine Doppelschenkelfeder, deren Zwischenschenkel am Lagergehäuse des variablen Ventiltriebs befestigt ist und deren Endschenkel gegen je einen die Anlagefläche bildenden Vorsprung zweier nebeneinander angeordneter Zwischenhebelglieder des Zwischenhebels vorgespannt anliegen. So werden beide Zwischenhebelglieder zweier nebeneinanderliegender Gaswechselventile mittels eines Federelementes in Richtung der drei Anlagepunkte belastet, wobei vorteilhafterweise die Kulissenrolle zwischen den beiden Zwischenhebelgliedern angeordnet ist.In a preferred embodiment, the spring element is a double leg spring, whose intermediate leg is attached to the bearing housing of the variable valve drive and whose end legs bear against each biased a projection forming the projection of two juxtaposed intermediate lever members of the intermediate lever. Thus, both intermediate lever members of two adjacent gas exchange valves are loaded by means of a spring element in the direction of the three contact points, wherein advantageously the sliding roller between the two intermediate lever members is arranged.
In einer bevorzugten Ausführungsform ist die Helix des Federelementes an der zur Nockenwelle und zum Rollenschlepphebel abgewandten Seite des Zwischenhebels angeordnet. Bei dieser Ausführung ist das Federelement aufgrund der guten Zugänglichkeit einfach zu montieren und gegebenenfalls zu wechseln.In a preferred embodiment, the helix of the spring element is arranged on the side facing away from the camshaft and the roller rocker arm side of the intermediate lever. In this embodiment, the spring element is easy to install and, if necessary, to change due to the good accessibility.
In einer alternativen vorteilhaften Ausführung ist die Helix des Federelementes an der zum Rollenschlepphebel gewandten Seite der Nockenwelle angeordnet, wodurch der benötigte Bauraum verringert wird.In an alternative advantageous embodiment, the helix of the spring element on the side facing the roller rocker arm is the Camshaft arranged, whereby the required space is reduced.
In einer hierzu weiterführenden Ausgestaltung der Erfindung ist die Helix im Bereich einer axialen Verlängerung einer Drehachse einer Rolle des Rollenschlepphebels angeordnet. Bei dieser Positionierung des Federelementes können in geeigneter Weise die gewünschten Kräfte und Drehmomente eingeleitet werden und andererseits das Federelement in kompakter Weise in den variablen Ventiltrieb integriert werden.In a further refinement of the invention, the helix is arranged in the region of an axial extension of a rotation axis of a roller of the roller cam follower. In this positioning of the spring element, the desired forces and torques can be introduced in a suitable manner and on the other hand, the spring element can be integrated in a compact manner in the variable valve train.
In einer wiederum weiterführenden Ausführung sind die beiden nebeneinander liegenden Rollenschlepphebel, die einer Doppelschenkelfeder zugeordnet sind zwischen den beiden Helices der Doppelschenkelfeder angeordnet, so dass eine gute Zugänglichkeit des Federelementes erhalten bleibt.In a further continuing embodiment, the two juxtaposed Rollenschlepphebel which are associated with a double leg spring between the two helices of the double leg spring are arranged so that a good accessibility of the spring element is maintained.
In einer alternativen Anordnung des Federelementes sind die beiden Helices der Doppelschenkelfeder zwischen den beiden nebeneinander liegenden Rollenschlepphebeln, die einer Doppelschenkelfeder zugeordnet sind, angeordnet, wodurch die Federschenkellängen verkürzt ausgebildet werden können.In an alternative arrangement of the spring element, the two helices of the double leg spring between the two juxtaposed Rollenschlepphebeln which are associated with a double leg spring, arranged, whereby the spring leg lengths can be formed shortened.
Es wird somit eine Federanordnung für einen variablen Ventiltrieb einer Verbrennungskraftmaschine geschaffen, mit der mittels nur eines Federelementes in allen drei gewünschten Anlagepunkten die benötigten Kontaktkräfte hergestellt werden und zusätzlich keine zu großen Kräfte auf Lager oder Rollen ausgeübt werden. Der Zwischenhebel wird zuverlässig positioniert, seine Lagerspiele kompensiert und ein Toleranzausgleich geschaffen. Dabei besteht ein geringer Montageaufwand und Bauraumbedarf.Thus, a spring arrangement is provided for a variable valve train of an internal combustion engine with which the required contact forces are produced by means of only one spring element in all three desired contact points and, in addition, no excessive forces are exerted on bearings or rollers. The intermediate lever is reliably positioned, its bearing clearances compensated and created a tolerance compensation. There is a low installation effort and space requirements.
Zwei Ausführungsbeispiele erfindungsgemäßer Federanordnungen für einen variablen Ventiltrieb einer Verbrennungskraftmaschine sind in den Figuren dargestellt und werden nachfolgend beschrieben.
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Figur 1 zeigt einen Ausschnitt einer ersten Ausführungsform einer erfindungsgemäßen Federanordnung für einen variablen Ventiltrieb in perspektivischer Darstellung, wobei die Motorgehäuseteile zum besseren Verständnis nicht dargestellt sind. -
Figur 2 zeigt einen Ausschnitt einer zweiten Ausführungsform einer erfindungsgemäßen Federanordnung für einen variablen Ventiltrieb in perspektivischer Darstellung, wobei die Motorgehäuseteile zum besseren Verständnis nicht dargestellt sind.
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FIG. 1 shows a detail of a first embodiment of a spring arrangement according to the invention for a variable valve train in a perspective view, wherein the motor housing parts are not shown for clarity. -
FIG. 2 shows a detail of a second embodiment of a spring arrangement according to the invention for a variable valve train in a perspective view, wherein the motor housing parts are not shown for clarity.
Der in den Figuren dargestellte variable Ventiltrieb besteht aus einer Nockenwelle 10, welche über einen Zwischenhebel 12 mit einem Rollenschlepphebel 14 wirkverbunden ist, der wiederum eine Verbindung zu einer Ventilstange 16 eines als Einlassventil dienenden Gaswechselventils 18 aufweist.The variable valve train shown in the figures consists of a
Bei dem dargestellten Ausführungsbeispiel handelt es sich um eine Verbrennungskraftmaschine mit zwei Einlassventilen pro Zylinder, denen jeweils ein Rollenschlepphebel 14 zugeordnet ist.In the illustrated embodiment, it is an internal combustion engine with two intake valves per cylinder, each associated with a
Um die Betätigungskraft der Nockenwelle 10 auf das Gaswechselventil 18 übertragen zu können, muss der Zwischenhebel 12 positioniert und geführt werden. Für eine vollständig definierte, geführte Kippbewegung zur Betätigung eines Gaswechselventils 18 muss der Zwischenhebel 12 drei Anlagepunkte aufweisen. Im vorliegenden Ausführungsbeispiel existieren insgesamt fünf Anlagepunkte, da zwei Gaswechselventile 18 über den einen Zwischenhebel 12 betätigt werden sollen, der hierzu zwei Zwischenhebelglieder 20 aufweist, die über eine gemeinsame Drehachse 22 miteinander verbunden sind, auf der im Innern der beiden Zwischenhebelglieder 20 jeweils eine Nockenwellenrolle 24 angeordnet ist und auf der zwischen den beiden Zwischenhebelgliedern 20 eine Kulissenrolle 26 angeordnet ist, die gegen eine Kulisse 28 anliegt, die am nicht dargestellten Lagergehäuse befestigt ist. Die anderen beiden Anlagepunkte bestehen zwischen einer Steuerwelle 30 sowie zwei Steuerwellenrollen 32, von denen je eine im Innern eines Zwischenhebelgliedes 20 angeordnet ist.In order to transmit the actuating force of the
Die beiden Steuerwellenrollen 32 sind in den Zwischenhebelgliedern 20 gelagert und befinden sich jeweils zwischen der Nockenwellenrolle 24 des jeweiligen Zwischenhebelgliedes 20 und einer am zur Nockenwellenrolle 24 entgegengesetzten Ende des Zwischenhebelgliedes 20 ausgebildeten Arbeitskurvenkontur 34, welche gegen eine Schlepphebelrolle 36 des Rollenschlepphebels 14 anliegt.The two
Bei Drehung der Nockenwelle 10 entsteht eine Kippbewegung des Zwischenhebels 12, wobei die Nockenwellenrolle 24 auf der Nockenwelle 10 abrollt, die Steuerwellenrolle 32 auf der Steuerwelle 30 abrollt und die Kulissenrolle 26 auf der feststehenden Kulisse 28 abrollt. Durch die Kippbewegung gleitet die Arbeitskurvenkontur 34 auf der Schlepphebelrolle 36 entlang, wodurch das zum festen gelagerten Ende 38 entgegengesetzte bewegliche Ende 40 des Rollenschlepphebels 14, gegen welches die Ventilstange 16 belastet ist, abgesenkt und bei Weiterdrehen wieder abgehoben wird.Upon rotation of the
Durch Drehen der Steuerwelle 30, auf der exzentrische Steuerflächen 42 ausgebildet sind, die gegen die Steuerwellenrollen 32 anliegen, wird der an der Schlepphebelrolle 36 angreifende Abschnitt der Arbeitskurvenkontur 34 geändert, da der Zwischenhebel 12 in eine andere Ausgangsposition gekippt wird. So können unterschiedliche Öffnungs- und Schließcharakteristiken der Gaswechselventile 18 erreicht werden.By rotating the
Zur korrekten Funktion dieses Ventiltriebes ist es erforderlich, dass eine ständige feste Anlage mit einer ausreichenden, jedoch nicht zu großen Anpresskraft zwischen der Nockenwelle 10 und der Nockenwellenrolle 24, der Steuerwelle 30 und der Steuerwellenrolle 32 sowie der Kulisse 28 und der Kulissenrolle 26 in jedem Betriebszustand, also in allen Nockenpositionen der Steuerwelle 30 und der Nockenwelle 10 sichergestellt wird.For proper operation of this valve train, it is necessary that a permanent fixed system with a sufficient, but not too large contact force between the
Hierzu wird erfindungsgemäß ein Federelement 44 in Form einer Doppelschenkelfeder verwendet. Diese weist zwei gegensinnig gewickelte Helices 46 auf, die über einen Zwischenschenkel 48 mit einer U-förmigen Umkehrung miteinander verbunden sind. Am jeweils anderen Ende der Helices 46 weist das Federelement 44 Endschenkel 50 auf.For this purpose, a
Erfindungsgemäß wird dieses Federelement 44 so angeordnet und ausgebildet, dass ihr Zwischenschenkel 48 in einer am Lagergehäuse fest angeordneten Zwischenschenkelaufnahme 52 befestigt ist, welche zwischen den beiden Zwischenhebelgliedern 20, der Kulisse 28 und den Rollenschlepphebeln 14 angeordnet ist. Von hier aus erstrecken sich die Drähte des Federelementes in entgegengesetzte axiale Richtungen bis zur jeweiligen zur Zwischenschenkelaufnahme 52 entgegengesetzten Seite der Rollenschlepphebel 14. Etwa in Verlängerung der Achse 35 der Schlepphebelrollen 36 ist somit außerhalb des Zwischenhebels 12 die jeweilige Helix 46 des Federelementes ausgebildet. Von den Helices 46 erstrecken sich jeweils die Endschenkel 50 des Federelementes 44 etwa in Erstreckungsrichtung der Zwischenhebelglieder 20 und zwar bis zum Ende der Zwischenhebelglieder 20 jenseits der Achse 22 der Nockenwellenrollen 24, wo jeweils ein Vorsprung 54 ausgebildet ist, der eine Anlagefläche 56 aufweist, gegen die ein umgebogenes Ende 58 des Endschenkels 50 in Richtung der Nockenwelle 10 vorgespannt anliegt.According to the invention, this
Durch die Vorspannung des Federelementes 44 wird der Zwischenhebel 12 beziehungsweise die Nockenwellenrolle 24 gegen die Nockenwelle 10 gedrückt und die Kulissenrolle 26 in die Kulissenbahn 28 gedrückt. Entsprechend ist der Vorsprung 54 so am Zwischenhebel 12 anzuordnen, dass eine Komponente der Federkraft in Richtung der Kulisse 28 zeigt. Neben dieser Anpresskraft durch das Federelement 44 entsteht jedoch auch ein Drehmoment um die Drehachse 22 der Nockenwellenrolle 24 beziehungsweise des Zwischenhebels 12, welches dazu führt, dass die Steuerwellenrolle 32 gegen die Steuerwelle 30 gedrückt wird.By the bias of the
Entsprechend wird durch das Federelement 44 eine definierte Position des Zwischenhebels 12 über die drei beziehungsweise fünf Auflagepunkte am Zwischenhebel 12 hergestellt. Dabei wird die ohnehin durch hohe Kräfte im Betrieb belastete Steuerwellenrolle 32 beziehungsweise Steuerwelle 30 nicht durch zu große Kräfte belastet, wie dies der Fall wäre, wenn die Kraft von der entgegen gesetzten Seite des Zwischenhebels 12 eingeleitet werden würde.Accordingly, the
Eine im Wesentlichen gleich wirkende Ausführungsform ist in der
Dieses Federelement 44 weist im Vergleich zur ersten Ausführungsform zwei Helices 46 auf, die sich unmittelbar axial nebeneinander befinden, so dass die Achse der Helices 46 ebenso wie der Zwischenschenkel 48 zwischen der Kulisse 28, der Nockenwelle 10, den beiden Zwischenhebelgliedern 20 und den Rollenschlepphebeln 14 angeordnet ist und sich an der zur Steuerwelle 30 entgegengesetzten Seite des Zwischenhebels 12 befindet.This
Die Endschenkel 50 weisen zwischen den beiden Zwischenhebelgliedern 20 an diesen vorbei und greifen vorgespannt hinter einen Vorsprung 54, der an der zur Nockenwelle 10 und im Wesentlichen auch zu Arbeitskurvenkontur 34 entgegengesetzten Seite des jeweiligen Zwischenhebelgliedes 20. Auch dieser Vorsprung 54 ist so angeordnet, dass der entstehende Kraftvektor eine Komponente aufweist, die in Richtung der Nockenwelle 10 zeigt und eine Komponente aufweist, die in Richtung der Kulisse 28 zeigt. Gleichzeitig wird ein Drehmoment um die Achse 22 erzeugt, durch welches eine Anpresskraft zwischen der Steuerwellenrolle 32 und Steuerwelle 30 entsteht.The
Dieses Federelement ist zwar etwas aufwendiger zu montieren, benötigt jedoch weniger Bauraum. In beiden Ausführungsbeispielen wird eine sichere Anlage des Zwischenhebels in den geforderten Auflagepunkten mit nur einem Federelement sichergestellt. Dabei sind die Anpresskräfte so verteilt, dass keine Überlastung der Rollen oder Lagerungen zu befürchten ist. Der Montageaufwand und der benötigte Bauraum sind minimiert.Although this spring element is somewhat more expensive to assemble, it requires less installation space. In both embodiments, a secure system of the intermediate lever is ensured in the required support points with only one spring element. The contact forces are distributed so that no overloading of the rollers or bearings is to be feared. The installation effort and the required installation space are minimized.
Es sollte deutlich sein, dass verschiedene Ausführungsformen der erfindungsgemäßen Federanordnung möglich sind, die sich von den beschriebenen Versionen unterscheiden. Beispielsweise können die beiden Helices auch oberhalb der Kulisse an der zur Nockenwelle entgegengesetzten Seite angeordnet werden und hinter den entsprechenden Vorsprung greifen um einerseits die Anpresskraft gegen die Nockenwelle und die Kulisse und andererseits das Drehmoment um die Nockenwellenrollenachse zu erzeugen, durch welche die Steuerwellenrolle gegen die Steuerwelle belastet wird. Auch kann sich die Federanordnung für anders aufgebaute variable Ventiltriebe beziehungsweise Motoren eignen, so dass beispielsweise eine andere Anzahl an Einlassventilen pro Zylinder benötigt wird. Weitere geänderte Anordnungen sind innerhalb des Schutzbereiches des Hauptanspruchs denkbar.It should be clear that various embodiments of the spring arrangement according to the invention are possible, which differ from the versions described. For example, the two helices can also be arranged above the gate on the opposite side to the camshaft and engage behind the corresponding projection on the one hand to generate the contact force against the camshaft and the link and on the other hand the torque about the camshaft axis, through which the control shaft roller against the control shaft is charged. Also, the spring assembly for differently constructed variable valve trains or engines are suitable, so that, for example, a different number of intake valves per cylinder is needed. Further modified arrangements are conceivable within the scope of the main claim.
Claims (7)
- A spring arrangement for a variable valve drive of an internal combustion engine having
an intermediate lever (12),
at least one camshaft roller (24) on the intermediate lever (12), which camshaft roller (24) bears against a camshaft (10),
a slotted roller (26) on the intermediate lever (12), which slotted roller (26) bears against a slotted guide (28),
at least one control shaft roller (32) on the intermediate lever (12), which control shaft roller (32) bears against a control shaft (30) and is arranged on that side of the camshaft roller (24) which faces away from the slotted guide (28),
at least one working cam contour (34) which is formed at that end of the intermediate lever (12) which lies opposite the camshaft roller (24) and acts on a roller drag lever (14) of a gas exchange valve (18), and
at least one spring element (44), via which the camshaft roller (24) of the intermediate lever (12) is loaded against the camshaft (10) and the slotted roller (26) is loaded against the slotted guide (28),
characterized in that
an end leg (50) of the spring element (44) bears in a prestressed manner against a contact surface (56) of the intermediate lever (12) on a side of the intermediate lever (12) which faces away from the working cam contour (34) and the camshaft (10), and the spring element (44) has a force component on the contact surface (56) in the direction of the camshaft (10) and in the direction of the slotted guide (28), wherein the contact surface (56) is arranged on the intermediate lever (12) on the side of an axis of rotation (22) of the camshaft roller (24) which faces away from the working cam contour (34) so that the spring element (44) generates a torque around the axis of rotation (22) of the camshaft roller (24) of the intermediate lever (12). - The spring arrangement for a variable valve drive of an internal combustion engine of claim 1, characterized in that the spring element (44) is a double-leg spring whose intermediate leg (48) is fastened to the bearing housing of the variable valve drive and whose end legs (50) bear in a prestressed manner against a respective protrusion (54) of two adjacently arranged intermediate lever members (20) of the intermediate lever (12), said respective protrusion forming the contact surface (56).
- The spring arrangement for a variable valve drive of an internal combustion engine of one of the preceding claims, characterized in that the helix (46) of the spring element (44) is arranged on the side of the intermediate lever (12) facing away from the camshaft (10) and the roller drag lever (14).
- The spring arrangement for a variable valve drive of an internal combustion engine of one of claims 1 or 2, characterized in that the helix (46) of the spring element (44) is arranged on the side of the camshaft (10) that is directed to the roller drag lever (14).
- A spring arrangement for a variable valve drive of an internal combustion engine of claim 4, characterized in that the helix (46) is arranged in the region of an axial projection of an axis (35) of a drag lever roller (36) of the roller drag lever (14).
- The spring arrangement for a variable valve drive of an internal combustion engine of claim 5, characterized in that the two adjacent roller drag levers (14), which are assigned to a double-leg spring (44), are arranged axially between the two helices (46) of the double-leg spring (44).
- The spring arrangement for a variable valve drive of an internal combustion engine of claim 5, characterized in that the two helices (46) of the double-leg spring (44) are arranged axially between the two adjacent roller drag levers (14) assigned to a double-leg spring (44).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310106646 DE102013106646A1 (en) | 2013-06-25 | 2013-06-25 | Spring arrangement for a variable valve train of an internal combustion engine |
PCT/EP2014/056799 WO2014206591A1 (en) | 2013-06-25 | 2014-04-04 | Spring arrangement for a variable valve drive of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3014080A1 EP3014080A1 (en) | 2016-05-04 |
EP3014080B1 true EP3014080B1 (en) | 2017-06-07 |
Family
ID=50439389
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14715302.7A Not-in-force EP3014080B1 (en) | 2013-06-25 | 2014-04-04 | Spring arrangement for a variable valve drive of an internal combustion engine |
Country Status (4)
Country | Link |
---|---|
US (1) | US9784142B2 (en) |
EP (1) | EP3014080B1 (en) |
DE (1) | DE102013106646A1 (en) |
WO (1) | WO2014206591A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016220397A1 (en) * | 2016-10-18 | 2017-08-10 | Schaeffler Technologies AG & Co. KG | Intermediate lever of a variable valve train |
EP3808968A1 (en) * | 2019-10-16 | 2021-04-21 | Volvo Car Corporation | An arrangement for transferring force from a camshaft to an output device |
DE102020101555A1 (en) * | 2020-01-23 | 2021-07-29 | Bayerische Motoren Werke Aktiengesellschaft | Stroke variable valve train with a double leg spring |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6868811B2 (en) * | 2002-06-13 | 2005-03-22 | Delphi Technologies, Inc. | Frameless variable valve actuation mechanism |
JP2004052604A (en) * | 2002-07-17 | 2004-02-19 | Kazuhiro Kanamaru | Valve drive mechanism of internal combustion engine, and intake air flow adjusting device thereof |
DE10235400A1 (en) | 2002-08-02 | 2004-02-19 | Bayerische Motoren Werke Ag | Cylinder head for an internal combustion engine with a variable stroke valve train |
DE102004003327A1 (en) * | 2004-01-22 | 2005-09-29 | Entec Consulting Gmbh | Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft |
JP4278590B2 (en) * | 2004-08-31 | 2009-06-17 | 株式会社日立製作所 | Variable valve operating device for internal combustion engine |
DE102004049538A1 (en) * | 2004-10-10 | 2006-04-13 | Rolf Jung | Fully variable lift valve controller for internal combustion engine has intermediate element in form of pivotable rocker arm acted upon by cam or camshaft at first engagement surface with control block at free end |
DE102004058106A1 (en) * | 2004-12-01 | 2006-06-08 | Rolf Jung | Fully variable lifting valve controller for combustion engine has intermediate element with rocker arm interacting with pawl in pivotable manner at coupling axis, acted upon by cam/camshaft at engagement surface, control block at free end |
DE102005040959A1 (en) * | 2005-08-30 | 2007-03-08 | Bayerische Motoren Werke Ag | Hubvariabler valve drive for an internal combustion engine |
DE102007047582A1 (en) | 2007-10-04 | 2009-04-09 | Hydraulik-Ring Gmbh | Device for controlling the residual gas content of cylinders of an internal combustion engine |
DE102010009399A1 (en) * | 2010-02-26 | 2011-09-01 | Schaeffler Technologies Gmbh & Co. Kg | Operating lever for stroke-variable gas exchange valve gear of internal-combustion engine, has lever housing, which is formed with two side panels and base, which is connected with side panels |
DE102010048708A1 (en) | 2010-10-19 | 2012-04-19 | Kolbenschmidt Pierburg Innovations Gmbh | Mechanically controllable valve train |
DE102012002026A1 (en) * | 2012-02-03 | 2013-08-08 | Volkswagen Aktiengesellschaft | Variable-stroke valve drive for internal combustion engine, has eccentric shaft with eccentric cams having angular range, in which stroke of valve and of similar valve group vary differently from each other |
-
2013
- 2013-06-25 DE DE201310106646 patent/DE102013106646A1/en not_active Ceased
-
2014
- 2014-04-04 US US14/899,560 patent/US9784142B2/en not_active Expired - Fee Related
- 2014-04-04 EP EP14715302.7A patent/EP3014080B1/en not_active Not-in-force
- 2014-04-04 WO PCT/EP2014/056799 patent/WO2014206591A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
US20160146066A1 (en) | 2016-05-26 |
EP3014080A1 (en) | 2016-05-04 |
US9784142B2 (en) | 2017-10-10 |
WO2014206591A1 (en) | 2014-12-31 |
DE102013106646A1 (en) | 2015-01-08 |
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