EP3006684B1 - Mechanically controllable valve drive and mechanically controllable valve drive assembly - Google Patents

Mechanically controllable valve drive and mechanically controllable valve drive assembly Download PDF

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Publication number
EP3006684B1
EP3006684B1 EP15180950.6A EP15180950A EP3006684B1 EP 3006684 B1 EP3006684 B1 EP 3006684B1 EP 15180950 A EP15180950 A EP 15180950A EP 3006684 B1 EP3006684 B1 EP 3006684B1
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EP
European Patent Office
Prior art keywords
valve drive
mechanically controllable
controllable valve
drive assembly
pivot lever
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EP15180950.6A
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German (de)
French (fr)
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EP3006684A1 (en
Inventor
Christoph Sadowski
Dr. Michael Breuer
Stefan Moormann
Dr. Karsten Grimm
Martin Lauterbach
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Pierburg GmbH
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Pierburg GmbH
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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

Definitions

  • the invention relates to a mechanically controllable valve train arrangement for at least one multi-cylinder row of an internal combustion engine having at least two cylinders, in each of which at least one gas exchange valve is provided, each of which acts on a transmission arrangement by means of an end face, wherein the transmission arrangement is movably mounted in the cylinder head by means of bearing means and wherein the transmission arrangement is in operative connection with a Ventilhubverstell sexual and a camshaft, wherein the Ventilhubverstell responded rotatable adjusting members having at least one eccentric member which acts on the transmission assembly against a biasing force of a spring member, such that different Ventilhubpositionen are adjustable, the Ventilhubverstell observed at least one actuator for a cylinder such that various valve lift positions, such as zero stroke, partial lift and full stroke adjust are bar.
  • Valve trains and such valve train arrangements are well known from the prior art.
  • the EP 638 706 A1 to control or regulate the valve lift a rotatably mounted in a cylinder head eccentric shaft, which acts on the transmission arrangement such that in a simple way valve strokes between 0 and can be set to a maximum.
  • the combustion process can be easily adapted to the respective operating state of the internal combustion engine.
  • it is from the DE 10 2004 003 327 A1 known to provide adjusting members in a valve train assembly that can be adjusted independently with the aim of individual cylinders for to shut down certain operating conditions.
  • the EP 1 760 278 A2 a valve train known, which has an eccentric member having different curves, in particular for the partial stroke and the full stroke. A zero-stroke curve is also made possible by the adjustment.
  • valve trains / valve train arrangements have the disadvantage that an adjustment of the valve lift via the Exzenterorgankurve must be very accurate.
  • variability of the valve lift settings in the known valve train arrangements in a partial cylinder shutdown is very limited, which in turn leads to increased fuel consumption and thus also to higher emissions.
  • Solutions for valve train arrangements are known in which the adjusting member has at least one eccentric member in the circumferential direction. But even hereby is a fast adjustment at an engine speed of, for example, 3000 / min within a base circle phase of the camshaft from maximum lift to minimum stroke can not be realized.
  • the object of the invention is therefore to provide a valve train or a valve train arrangement, the / o.g. Disadvantage in a simple and inexpensive way avoids.
  • each cylinder is associated with at least one actuator, wherein the actuators are operatively connected via a reduction gear transmission with the adjusting member, wherein the gear transmission of a spur gear and a worm gear is constructed, wherein a Schneckenradwelle is provided and wherein Adjusting member is at least partially designed as a worm wheel ..
  • a particularly advantageous embodiment is provided in that the reduction is between 5/1 and 10/1.
  • a small cost-effective actuator with low inertia can be used.
  • this reduces the problem of inertia even further, since the Aktuatorflamiere can reduce.
  • the worm wheel shaft is mounted above and below the adjusting member.
  • the adjusting member may advantageously have an eccentric member designed as a control cam.
  • each transmission arrangement has at least one pivot lever arrangement and at least one rocker arm, wherein a pivot lever of the pivot lever assembly engages with an end face on the gas exchange valve and the rocker arm is in operative connection with the Ventilhubverstell issued and a camshaft and over a working curve on the pivot lever attacks.
  • FIG. 1 shows an embodiment of a valve train assembly 10 according to the invention of a 4-cylinder in-line engine with a gas inlet side 12 and a gas outlet side 14, which are each assigned in a known manner a cylinder, not shown.
  • gas inlet and outlet valves have been omitted. In the following description should be limited to a gas inlet side 12.
  • the gas inlet valves, not shown are associated in a known manner pivot lever assemblies 16, 18, 20, 22, 24, 26, 28, 30, wherein in each case a pivot lever assembly is in operative connection with a gas exchange valve.
  • the pivot lever arrangements 16, 18, 20, 22, 24, 26, 28, 30 are part of eight transmission arrangements 32, 34, 36, 38, 40, 42, 44, 46, on each of which a pivot lever arrangement 16, 18, 20, 22, 24, 26, 28, 30 is assigned.
  • the transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 are mounted in a known manner in the cylinder head by means not shown bearing means.
  • the transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 in a known manner with a camshaft 48 in operative connection.
  • each transmission assembly 32, 34, 36, 38, 40, 42, 44, 46 by adjusting members 50, 52, 54, 56, 58, 60, 62, 64, each having an eccentric member 51 (see FIG.
  • a Ventilhubverstell disturbing 66 can be controlled such that a lesser, higher valve lift or even a shutdown of the gas inlet valves is adjustable.
  • the eccentric member 51 of each adjusting member 50, 52, 54, 56, 58, 60, 62, 64 designed as a control cam, wherein two adjusting members 50, 52, 54, 56, 58, 60, 62, 64 on a Shaft section 68, 70, 72, 74 are provided.
  • each shaft section 68, 70, 72, 74 is in operative connection with an actuator 76, 78, 80, 82.
  • the Ventilhubverstell familiar 66 is in the present embodiment with respect to the gas inlet side 12 thus four actuators 76, 78, 80, 82, four shaft sections 68, 70, 72, 74, each with two adjusting members 50, 52, 54, 56, 58, 60, 62, 64, wherein the shaft portions 68, 70, 72, 74, as shown in FIG. 2 explained, transmission technology with the actuators 76, 78, 80, 82 are coupled.
  • a transmission assembly 32 has a pivot lever assembly 16 with a pivot lever 84 and a rocker arm 86, wherein the pivot lever 84 engages in a known manner with an end face on a gas inlet valve and the rocker arm 86 is in operative connection with the Ventilhubverstell responded 66 and the camshaft 48.
  • the adjusting member 50 of the Ventilhubverstell aggr 66 engages against a biasing force of a spring, not shown on an engaging member 88 (for example, a roller) of the rocker arm 86 at.
  • the rocker arm 86 engages with a working curve 90 not shown (see FIG. 2 ) on the pivot lever 84 at.
  • FIG. 2 shows now in a side view of the Sprinthielungsan Aunt 32.
  • the power is transmitted to the pivot lever assembly 16 due to the camshaft rotation of the camshaft 48.
  • a cam 104 of the camshaft 48 engages the roller 102 at.
  • the actuator 76 is provided, which is operatively connected via a reduction gear transmission 106 with the shaft portion 68 and thus with the adjusting member 50.
  • the gear transmission 106 consists in the present embodiment of a straight spur gear 108 and a worm gear 110, wherein a worm wheel 112 is provided, the screw gear via a worm gear 114 indirectly via the shaft portion 68 with the adjusting member 50 is engaged. In the present embodiment, this ensures a reduction of 7: 1. Characterized in that the worm wheel shaft 112 is mounted above and below the adjusting member 50 via bearing means 116, 118, the flexural rigidity is increased.

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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 einen mechanisch steuerbare Ventiltriebanordnung für mindestens eine mehrzylindrige Reihe einer Brennkraftmaschine, die mindestens zwei Zylinder aufweist, in denen jeweils mindestens ein Gaswechselventil vorgesehen ist, auf das jeweils eine Übertragungsanordnung mittels einer Stirnfläche angreift, wobei die Übertragungsanordnung im Zylinderkopf mittels Lagermittel beweglich gelagert ist und wobei die Übertragungsanordnung mit einer Ventilhubverstelleinrichtung und einer Nockenwelle in Wirkverbindung steht, wobei die Ventilhubverstelleinrichtung drehbare Verstellorgane mit mindestens einem Exzenterorgan aufweist, das auf die Übertragungsanordnung entgegen einer Vorspannkraft eines Federorgans einwirkt, derart, dass verschiedene Ventilhubpositionen einstellbar sind, wobei die Ventilhubverstelleinrichtung mindestens einen Aktuator für einen Zylinder aufweist, derart, dass verschiedene Ventilhubpositionen, wie zum Beispiel Nullhub, Teilhub und Vollhub einstellbar sind.The invention relates to a mechanically controllable valve train arrangement for at least one multi-cylinder row of an internal combustion engine having at least two cylinders, in each of which at least one gas exchange valve is provided, each of which acts on a transmission arrangement by means of an end face, wherein the transmission arrangement is movably mounted in the cylinder head by means of bearing means and wherein the transmission arrangement is in operative connection with a Ventilhubverstelleinrichtung and a camshaft, wherein the Ventilhubverstelleinrichtung rotatable adjusting members having at least one eccentric member which acts on the transmission assembly against a biasing force of a spring member, such that different Ventilhubpositionen are adjustable, the Ventilhubverstelleinrichtung at least one actuator for a cylinder such that various valve lift positions, such as zero stroke, partial lift and full stroke adjust are bar.

Ventiltriebe sowie derartige Ventiltriebanordnungen sind aus dem Stand der Technik hinlänglich bekannt. So offenbart beispielsweise die EP 638 706 A1 zur Steuerung bzw. Regelung des Ventilhubes eine in einem Zylinderkopf drehbar gelagerte Exzenterwelle, die auf die Übertragungsanordnung derartig einwirkt, dass auf einfache Weise Ventilhübe zwischen 0 und maximal eingestellt werden können. Durch diese Maßnahme kann der Verbrennungsprozess gut dem jeweiligen Betriebszustand der Brennkraftmaschine angepasst werden. Darüber hinaus ist es aus der DE 10 2004 003 327 A1 bekannt, bei einer Ventiltriebanordnung Verstellorgane vorzusehen, die unabhängig voneinander verstellt werden können mit dem Ziel, einzelne Zylinder für bestimmte Betriebszustände still zu legen. Desweiteren ist aus der EP 1 760 278 A2 ein Ventiltrieb bekannt, der ein Exzenterorgan besitzt, das verschiedene Kurvenverläufe insbesondere für den Teilhub und den Vollhub, aufweist. Ein Nullhub-Kurvenverlauf wird durch das Verstellorgan dabei ebenfalls ermöglicht.Valve trains and such valve train arrangements are well known from the prior art. For example, the EP 638 706 A1 to control or regulate the valve lift a rotatably mounted in a cylinder head eccentric shaft, which acts on the transmission arrangement such that in a simple way valve strokes between 0 and can be set to a maximum. By this measure, the combustion process can be easily adapted to the respective operating state of the internal combustion engine. In addition, it is from the DE 10 2004 003 327 A1 known to provide adjusting members in a valve train assembly that can be adjusted independently with the aim of individual cylinders for to shut down certain operating conditions. Furthermore, from the EP 1 760 278 A2 a valve train known, which has an eccentric member having different curves, in particular for the partial stroke and the full stroke. A zero-stroke curve is also made possible by the adjustment.

Diese bekannten Ventiltriebe/Ventiltriebanordnungen weisen jedoch den Nachteil auf, dass eine Verstellung des Ventilhubes über die Exzenterorgankurve sehr genau erfolgen muss. Außerdem ist die Variabilität der Ventilhubeinstellungen bei den bekannten Ventiltriebanordnungen bei einer teilweisen Zylinderabschaltung sehr eingegrenzt, was wiederum zu einem erhöhten Kraftstoffverbrauch und damit auch zu höheren Emissionswerten führt. Aus der DE 10 2010 048 709 B4 und der DE 2006 033 559 A1 sind Lösungen für Ventiltriebanordnungen bekannt, bei denen das Verstellorgan in Umfangsrichtung mindestens ein Exzenterorgan aufweist. Aber auch hiermit ist eine schnelle Verstellung bei einer Motordrehzahl von beispielsweise 3000/min innerhalb einer Grundkreisphase der Nockenwelle von maximalem Hub zu minimalem Hub nicht zu realisieren.However, these known valve trains / valve train arrangements have the disadvantage that an adjustment of the valve lift via the Exzenterorgankurve must be very accurate. In addition, the variability of the valve lift settings in the known valve train arrangements in a partial cylinder shutdown is very limited, which in turn leads to increased fuel consumption and thus also to higher emissions. From the DE 10 2010 048 709 B4 and the DE 2006 033 559 A1 Solutions for valve train arrangements are known in which the adjusting member has at least one eccentric member in the circumferential direction. But even hereby is a fast adjustment at an engine speed of, for example, 3000 / min within a base circle phase of the camshaft from maximum lift to minimum stroke can not be realized.

Aufgabe der Erfindung ist es daher, einen Ventiltrieb bzw. eine Ventiltriebanordnung zu schaffen, der/die den o.g. Nachteil auf einfache und kostengünstige Weise vermeidet.The object of the invention is therefore to provide a valve train or a valve train arrangement, the / o.g. Disadvantage in a simple and inexpensive way avoids.

Diese Aufgabe wird dadurch gelöst, dass jedem Zylinder mindestens ein Aktuator zugeordnet ist, wobei die Aktuatoren über ein Untersetzungs-Zahnradgetriebe mit dem Verstellorgan wirkverbunden sind, wobei das Zahnradgetriebe aus einem geradverzahnten Stirnradgetriebe und einem Schneckenradgetriebe aufgebaut ist, wobei eine Schneckenradwelle vorgesehen ist und wobei das Verstellorgan zumindest teilweise als Schneckenrad ausgebildet ist.. Auf diese Weise ist es zunächst möglich in der lastfreien Grundkreisphase das Gaswechselventil eines Ventiltriebs an zu steuern. Darüber hinaus wird eine kostengünstige Lösung geschaffen, den Kraftstoffverbrauch und die Emissionswerte eines Verbrennungsmotors durch die Erhöhung der Variabilität eines Gaswechselventils zu senken, wobei der Aktuator von den Axialkräften an der Zwischenwelle entkoppelt ist.This object is achieved in that each cylinder is associated with at least one actuator, wherein the actuators are operatively connected via a reduction gear transmission with the adjusting member, wherein the gear transmission of a spur gear and a worm gear is constructed, wherein a Schneckenradwelle is provided and wherein Adjusting member is at least partially designed as a worm wheel .. In this way, it is initially possible in the load-free base circle phase to the gas exchange valve of a valve train to control. In addition, a cost effective solution is provided to reduce fuel consumption and emissions of an internal combustion engine by increasing the variability of a gas exchange valve, wherein the actuator is decoupled from the axial forces on the intermediate shaft.

Eine besonders vorteilhafte Ausführungsform wird dadurch geschaffen, dass die Untersetzung zwischen 5/1 und 10/1 beträgt. Hierdurch kann ein kleiner kostengünstiger Aktuator mit geringen Massenträgheiten eingesetzt werden. Zudem wird hierdurch das Problem der Massenträgheiten noch weiter gemindert, da sich die Aktuatordrehzahl vermindern kann. In einer besonderen Ausführungsform ist die Schneckenradwelle oberhalb und unterhalb des Verstellorgans gelagert. Desweiteren kann in vorteilhafter Weise das Verstellorgan ein als Steuernocken ausgebildetes Exzenterorgan aufweisen.A particularly advantageous embodiment is provided in that the reduction is between 5/1 and 10/1. As a result, a small cost-effective actuator with low inertia can be used. In addition, this reduces the problem of inertia even further, since the Aktuatordrehzahl can reduce. In a particular embodiment, the worm wheel shaft is mounted above and below the adjusting member. Furthermore, the adjusting member may advantageously have an eccentric member designed as a control cam.

Eine besonders vorteilhafte mechanisch steuerbare Ventiltriebanordnung wird darüber hinaus dadurch geschaffen, dass jede Übertragungsanordnung mindestens eine Schwenkhebelanordnung und mindestens einen Kipphebel aufweist, wobei ein Schwenkhebel der Schwenkhebelanordnung mit einer Stirnfläche an dem Gaswechselventil angreift und der Kipphebel in Wirkverbindung mit der Ventilhubverstelleinrichtung und einer Nockenwelle steht und über eine Arbeitskurve an dem Schwenkhebel angreift.A particularly advantageous mechanically controllable valve train arrangement is moreover created in that each transmission arrangement has at least one pivot lever arrangement and at least one rocker arm, wherein a pivot lever of the pivot lever assembly engages with an end face on the gas exchange valve and the rocker arm is in operative connection with the Ventilhubverstelleinrichtung and a camshaft and over a working curve on the pivot lever attacks.

Die Erfindung wird nachfolgend anhand der Zeichnung näher erläutert, hierin zeigen:

  • Figur 1 eine perspektivische Darstellung einer erfinderischen Ventiltriebanordnung, und
  • Figur 2 eine Seitenansicht einer erfindungsgemäßen Ventiltriebes mit einer Übertragungsanordnung.
The invention will be explained in more detail below with reference to the drawing, in which:
  • FIG. 1 a perspective view of an inventive valve train assembly, and
  • FIG. 2 a side view of a valve gear according to the invention with a transmission arrangement.

Figur 1 zeigt eine Ausführungsform einer erfindungsgemäßen Ventiltriebanordnung 10 eines 4-Zylinder-Reihenmotors mit einer Gaseinlassseite 12 und einer Gasauslassseite 14, die jeweils auf bekannte Weise einem nicht dargestellten Zylinder zugeordnet sind. Der Übersichtlichkeit halber sind Gaseinlass- und Gasauslassventile weggelassen worden. Bei der nachfolgenden Beschreibung soll sich doch auf eine Gaseinlassseite 12 beschränkt werden. Den nicht dargestellten Gaseinlassventilen sind auf bekannte Weise Schwenkhebelanordnungen 16, 18, 20, 22, 24, 26, 28, 30 zugeordnet, wobei jeweils ein Schwenkhebelanordnung mit einem Gaswechselventil in Wirkverbindung steht. Die Schwenkhebelanordnungen 16, 18, 20, 22, 24, 26, 28, 30 sind Teil von acht Übertragungsanordnungen 32, 34, 36, 38, 40, 42, 44, 46, auf, denen jeweils eine Schwenkhebelanordnung 16, 18, 20, 22, 24, 26, 28, 30 zugeordnet ist. Dabei sind die Übertragungsanordnungen 32, 34, 36, 38, 40, 42, 44, 46 auf bekannte Weise im Zylinderkopf mittels nicht weiter dargestellten Lagermitteln gelagert. Darüber hinaus stehen die Übertragungsanordnungen 32, 34, 36, 38, 40, 42, 44, 46 auf bekannte Weise mit einer Nockenwelle 48 in Wirkverbindung. Außerdem ist jede Übertragungsanordnung 32, 34, 36, 38, 40, 42, 44, 46 durch Verstellorgane 50, 52, 54, 56, 58, 60, 62, 64, die jeweils ein Exzenterorgan 51 aufweisen (siehe hierzu Figur 2), einer Ventilhubverstelleinrichtung 66 derart ansteuerbar, dass ein geringerer, höherer Ventilhub oder gar eine Abschaltung der Gaseinlassventile einstellbar ist. Im vorliegenden Ausführungsbeispiel ist das Exzenterorgan 51 eines jeden Verstellorganes 50, 52, 54, 56, 58, 60, 62, 64 als Steuernocken ausgeführt, wobei jeweils zwei Verstellorgane 50, 52, 54, 56, 58, 60, 62, 64 auf einem Wellenabschnitt 68, 70, 72, 74 vorgesehen sind. Hierbei steht jeder Wellenabschnitt 68, 70, 72, 74 mit einem Aktuator 76, 78, 80, 82 in Wirkverbindung. Die Ventilhubverstelleinrichtung 66 besteht im vorliegendem Ausführungsbeispiel bezogen auf die Gaseinlassseite 12 also aus vier Aktuatoren 76, 78, 80, 82, vier Wellenabschnitten 68, 70, 72, 74 mit jeweils zwei Verstellorgane 50, 52, 54, 56, 58, 60, 62, 64, wobei die Wellenabschnitte 68, 70, 72, 74, wie unter Figur 2 erläutert, getriebetechnisch mit den Aktuatoren 76, 78, 80, 82 gekoppelt sind. FIG. 1 shows an embodiment of a valve train assembly 10 according to the invention of a 4-cylinder in-line engine with a gas inlet side 12 and a gas outlet side 14, which are each assigned in a known manner a cylinder, not shown. For the sake of clarity, gas inlet and outlet valves have been omitted. In the following description should be limited to a gas inlet side 12. The gas inlet valves, not shown are associated in a known manner pivot lever assemblies 16, 18, 20, 22, 24, 26, 28, 30, wherein in each case a pivot lever assembly is in operative connection with a gas exchange valve. The pivot lever arrangements 16, 18, 20, 22, 24, 26, 28, 30 are part of eight transmission arrangements 32, 34, 36, 38, 40, 42, 44, 46, on each of which a pivot lever arrangement 16, 18, 20, 22, 24, 26, 28, 30 is assigned. The transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 are mounted in a known manner in the cylinder head by means not shown bearing means. In addition, the transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 in a known manner with a camshaft 48 in operative connection. In addition, each transmission assembly 32, 34, 36, 38, 40, 42, 44, 46 by adjusting members 50, 52, 54, 56, 58, 60, 62, 64, each having an eccentric member 51 (see FIG. 2 ), a Ventilhubverstelleinrichtung 66 can be controlled such that a lesser, higher valve lift or even a shutdown of the gas inlet valves is adjustable. In the present embodiment, the eccentric member 51 of each adjusting member 50, 52, 54, 56, 58, 60, 62, 64 designed as a control cam, wherein two adjusting members 50, 52, 54, 56, 58, 60, 62, 64 on a Shaft section 68, 70, 72, 74 are provided. In this case, each shaft section 68, 70, 72, 74 is in operative connection with an actuator 76, 78, 80, 82. The Ventilhubverstelleinrichtung 66 is in the present embodiment with respect to the gas inlet side 12 thus four actuators 76, 78, 80, 82, four shaft sections 68, 70, 72, 74, each with two adjusting members 50, 52, 54, 56, 58, 60, 62, 64, wherein the shaft portions 68, 70, 72, 74, as shown in FIG. 2 explained, transmission technology with the actuators 76, 78, 80, 82 are coupled.

Im Detail weist eine Übertragungsanordnung 32 eine Schwenkhebelanordnung 16 mit einem Schwenkhebel 84 sowie einem Kipphebel 86 auf, wobei der Schwenkhebel 84 auf bekannte Weise mit einer Stirnfläche an einem Gaseinlassventil angreift und der Kipphebel 86 in Wirkverbindung mit der Ventilhubverstelleinrichtung 66 und der Nockenwelle 48 steht. Dabei greift das Verstellorgan 50 der Ventilhubverstelleinrichtung 66 entgegen einer Vorspannkraft einer nicht dargestellten Feder an einem Angriffsorgan 88 (beispielsweise eine Rolle) des Kipphebels 86 an. Der Kipphebel 86 greift mit einer nicht weiter dargestellten Arbeitskurve 90 (siehe hierzu Figur 2) an dem Schwenkhebel 84 an. Auf der gegenüber gelegenen Seite sind Führungsrollen 92, 94 angeordnet, mit denen der Kipphebel 86 in zwei Kulissen 96, 98 geführt ist. In den Kulissen 96, 98 geführten Führungsrollen 92, 94 (siehe hierzu Figur 2) sind wiederum auf einer Welle 100 gelagert, wobei zwischen den Führungsrollen 92, 94 noch eine Rolle 102 auf der Welle 100 angeordnet ist, die wiederum mit der Nockenwelle 48 in Wirkverbindung steht. Ein Nocken 104 der Nockenwelle 48 steht also mit zwei Übertragungsanordnungen in Wirkverbindung.In detail, a transmission assembly 32 has a pivot lever assembly 16 with a pivot lever 84 and a rocker arm 86, wherein the pivot lever 84 engages in a known manner with an end face on a gas inlet valve and the rocker arm 86 is in operative connection with the Ventilhubverstelleinrichtung 66 and the camshaft 48. In this case, the adjusting member 50 of the Ventilhubverstelleinrichtung 66 engages against a biasing force of a spring, not shown on an engaging member 88 (for example, a roller) of the rocker arm 86 at. The rocker arm 86 engages with a working curve 90 not shown (see FIG. 2 ) on the pivot lever 84 at. On the opposite side guide rollers 92, 94 are arranged, with which the rocker arm 86 is guided in two scenes 96, 98. In the scenes 96, 98 guided guide rollers 92, 94 (see FIG. 2 ) are in turn mounted on a shaft 100, wherein between the guide rollers 92, 94 still a roller 102 is disposed on the shaft 100, which in turn is in operative connection with the camshaft 48. A cam 104 of the camshaft 48 is thus in operative connection with two transmission arrangements.

Figur 2 zeigt nun in einer Seitenansicht die Überragungsanordnung 32. Über die Arbeitskurve 90 des Kipphebels 86 erfolgt die Kraftübertragung auf die Schwenkhebelanordnung 16 aufgrund der Nockenwellendrehung der Nockenwelle 48. Hierzu greift ein Nocken 104 der Nockenwelle 48 auf die Rolle 102 an. FIG. 2 shows now in a side view of the Überragungsanordnung 32. About the working curve 90 of the rocker arm 86, the power is transmitted to the pivot lever assembly 16 due to the camshaft rotation of the camshaft 48. For this purpose, a cam 104 of the camshaft 48 engages the roller 102 at.

Um eine Ventilhubverstellung durch zu führen, ist der Aktuator 76 vorgesehen, der über ein Untersetzungs-Zahnradgetriebe 106 mit dem Wellenabschnitt 68 und damit mit dem Verstellorgan 50 wirkverbunden ist. Das Zahnradgetriebe 106 besteht im vorliegenden Ausführungsbeispiel aus einem geradverzahnten Stirnradgetriebe 108 und einem Schneckenradgetriebe 110, wobei eine Schneckenradwelle 112 vorgesehen ist, deren Schraubengang über ein Schneckenrad 114 mittelbar über den Wellenabschnitt 68 mit dem Verstellorgan 50 in Eingriff steht. Im vorliegenden Ausführungsbeispiel wird hierdurch eine Untersetzung von 7:1 gewährleistet. Dadurch, dass die Schneckenradwelle 112 oberhalb und unterhalb des Verstellorgans 50 über Lagermittel 116, 118 gelagert ist, wird die Biegesteifigkeit erhöht.To perform a valve lift adjustment, the actuator 76 is provided, which is operatively connected via a reduction gear transmission 106 with the shaft portion 68 and thus with the adjusting member 50. The gear transmission 106 consists in the present embodiment of a straight spur gear 108 and a worm gear 110, wherein a worm wheel 112 is provided, the screw gear via a worm gear 114 indirectly via the shaft portion 68 with the adjusting member 50 is engaged. In the present embodiment, this ensures a reduction of 7: 1. Characterized in that the worm wheel shaft 112 is mounted above and below the adjusting member 50 via bearing means 116, 118, the flexural rigidity is increased.

Claims (5)

  1. Mechanically controllable valve drive assembly for at least one multicylinder row of an internal combustion engine with at least two cylinders, each of which is provided with at least one gas exchange valve respectively engaged by a transmission arrangement (32, 34, 36, 38, 40, 42, 44, 46) by means of an end face, wherein the transmission arrangement (32, 34, 36, 38, 40, 42, 44, 46) is movably supported in the cylinder head by bearing means, and wherein the transmission arrangement (32, 34, 36, 38, 40, 42, 44, 46) is operatively connected to a valve lift adjustment means (66) and a camshaft (48), wherein the valve lift adjustment means (66) comprises rotatable adjustment elements (50, 52, 54, 56, 58, 60, 62, 64) with at least one eccentric element (51) which acts on the transmission arrangement (32) against the pre-tensioning force of a spring element such that different valve lift positions can be set, wherein the valve lift adjustment means (66) comprises at least one actuator (76, 78, 80, 82), characterized in that each cylinder has at least one actuator (76, 78, 80, 82) assigned thereto, wherein the actuators (76, 78, 80, 82) are operatively connected to the adjustment element (50, 52, 54, 56, 58, 60, 62, 64) via a reduction gearing (106), wherein the gearing (106) is formed by a straight spur gearing (108) and a worm gearing (110), wherein a worm gear shaft (112) is provided, and wherein the adjustment element (50) is at least partly configured as a worm gear (114).
  2. Mechanically controllable valve drive assembly of claim 1, characterized in that the reduction is between 5/1 and 10/1.
  3. Mechanically controllable valve drive assembly of claim 2, characterized in that the worm gear shaft (112) is supported above and below the adjustment elements (50, 52, 54, 56, 58, 60, 62, 64) by bearing means (116, 118).
  4. Mechanically controllable valve drive assembly of one of the preceding claims, characterized in that the adjustment element (50, 52, 54, 56, 58, 60, 62, 64) comprises an eccentric element (51) designed as a control cam.
  5. Mechanically controllable valve drive assembly of one of claims 1 to 4, characterized in that each transmission arrangement (32, 34, 36, 38, 40, 42, 44, 46) comprises at least one pivot lever arrangement (16, 18, 20, 22, 24, 26, 28, 30) and at least one rocker lever (86), wherein one pivot lever (84) of the pivot lever arrangement (16, 18, 20, 22, 24, 26, 28, 30) engages the gas exchange valve with an end face and the rocker lever (86) is operatively connected with the valve lift adjustment means (66) and a camshaft (48) and engages the pivot lever (84) via a working cam (90).
EP15180950.6A 2014-10-02 2015-08-13 Mechanically controllable valve drive and mechanically controllable valve drive assembly Active EP3006684B1 (en)

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DE102014114396.5A DE102014114396A1 (en) 2014-10-02 2014-10-02 Mechanically controllable valve drive and mechanically controllable valve train arrangement

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ES2642861T3 (en) 2017-11-20
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