EP2823158A1 - Mechanically controllable valve drive arrangement - Google Patents

Mechanically controllable valve drive arrangement

Info

Publication number
EP2823158A1
EP2823158A1 EP12809746.6A EP12809746A EP2823158A1 EP 2823158 A1 EP2823158 A1 EP 2823158A1 EP 12809746 A EP12809746 A EP 12809746A EP 2823158 A1 EP2823158 A1 EP 2823158A1
Authority
EP
European Patent Office
Prior art keywords
intermediate lever
arrangement
lever
operative connection
roller
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12809746.6A
Other languages
German (de)
French (fr)
Other versions
EP2823158B1 (en
Inventor
Martin Nowak
Karsten Grimm
Michael Breuer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kolbenschmidt Pierburg Innovations GmbH
Original Assignee
Kolbenschmidt Pierburg Innovations GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kolbenschmidt Pierburg Innovations GmbH filed Critical Kolbenschmidt Pierburg Innovations GmbH
Publication of EP2823158A1 publication Critical patent/EP2823158A1/en
Application granted granted Critical
Publication of EP2823158B1 publication Critical patent/EP2823158B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • 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
    • 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
    • F01L13/0026—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 by means of an eccentric
    • 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
    • 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 mechanically controllable valve train arrangement having a plurality of gas exchange valves arranged in series, which are assigned to corresponding cylinders, wherein a gas exchange valve is assigned a transmission arrangement, wherein the transmission arrangement has at least one intermediate lever arrangement and at least one pivot lever arrangement, wherein an intermediate lever of the intermediate lever arrangement with a working curve for operative connection with a pivot lever of the pivot lever assembly, wherein the intermediate lever is operatively connected to a circumferential contour of a camshaft and wherein the intermediate lever assembly comprises an engaging member which is in operative connection with a valve lift.
  • valve train arrangements are well known.
  • DE 10 2006 033 559 AI and DE 10 2007 022 266 AI valve train arrangements having an adjustable lift height of a gas exchange valve in question.
  • an intermediate lever arrangement is provided in both valve train arrangements, which is on the one hand in operative connection with a camshaft to move the gas exchange valve periodically, and on the other hand has an attacking member, via which the maximum or minimum reachable lifting height is adjustable.
  • all these valve train arrangements have the disadvantage that after production and subsequent assembly due to manufacturing tolerances a precisely desired valve lift is not adjustable or can not be restored in the operating state.
  • a precisely desired valve lift is not adjustable or can not be restored in the operating state.
  • Especially when requesting an identical valve lift across all valves and cylinders of a Multi-cylinder combustion engine can lead to unsatisfactory running behavior of the engine at low valve strokes.
  • the invention is therefore based on the object to design a mechanically controllable valve train arrangement such that the disadvantages described above can be avoided.
  • the Ventilhubverstell Marie has a control shaft which acts on a first end of a rotatably mounted in a bearing actuating lever, wherein the second end is in operative connection with the engaging member of the intermediate lever assembly.
  • the so-called lever it is much easier even in the preassembled or final assembled state to adjust the valve lift of the associated gas exchange valve.
  • the engagement member of the intermediate lever assembly may advantageously be formed by a surface portion on the intermediate lever, wherein advantageously the adjusting lever has a first rotatably mounted roller, which may be in operative connection with the surface portion of the intermediate lever.
  • the intermediate lever may advantageously have a second rotatably mounted roller, which is in operative connection with the control shaft to further minimize wear phenomena.
  • the intermediate lever on the working contour opposite side has a first roller, which is in operative connection with the camshaft, and has a second roller which in a Setting is performed, the attacking member is provided between the first roller and the working contour.
  • an intermediate lever assembly comprises two intermediate levers, which are connected via a connecting shaft at the opposite end of the working curve, wherein first rollers are provided for the transmission of a camshaft to the intermediate lever and a second roller between the intermediate levers is provided for guidance in a backdrop, wherein the attacking member is formed by thembisweife.
  • Figure 1 is a perspective view of an inventive valve train assembly that works on the basic principle "Univalve”, and
  • Figure 2 is a schematic side view of an embodiment according to the invention of a valve train assembly for a gas exchange valve.
  • FIG. 1 shows an embodiment of a valve train arrangement 10 according to the invention with a plurality of gas exchange valves 12, 14, 16, 18, 20, 22, 24 and 26 arranged in series.
  • the mechanically controllable valve train arrangement 10 has in the present case four transmission arrangements 28, 29, 30, 31, 32, 33 and 34, 35, which in each case two gas exchange valves 12, 14; 16, 18; 20, 22; 24, 26 are assigned.
  • the transmission arrangements 28, 29, 30, 31, 32, 33 and 34, 35 are mounted in a known manner in the cylinder head by means of bearing means.
  • the bearing means 36, 38 are shown in the present figure, only by way of example for the storage of a pivot lever 56 of the transfer assembly 35.
  • each transmission assembly 28, 29, 30, 31, 32, 33 and 34, 35 in known manner with a camshaft 40 in operative connection.
  • each transmission assembly 28, 29, 30, 31, 32, 33 and 34, 35 by adjusting members 42, 43, 44, 45, 46, 47 and 48, 49 of a Ventifhubverstell 180 41 can be controlled such that a lesser or higher valve lift of the intake valves 12, 14, 16, 18, 20, 22, 24, 26 is adjustable.
  • the adjusting members 42, 43, 44, 45, 46, 47 and 48, 49 are each two inlet valves 12, 14; 16, 18; 20, 22; Assigned 24, 26 and executed as control organs, which are provided on a Steuerweile 50 and act on attack elements 75.
  • the control shaft 50 is designed here as an eccentric shaft.
  • control shaft 50 may have any type of drive contours.
  • the Ventilhubversteilinnate 41 is driven in the present embodiment by a drive member 52 in a known manner.
  • a drive member 52 both a forward and reverse running rotary drive can be used.
  • the Ventilhubversteilinnate 41 can thus be driven in such a way that depending on the present position quickly and precisely the valve operating stroke corresponding to the next operating state can be selected by the use of the corresponding control elements. Even angles of rotation of> 360 ° can be realized.
  • a mechanically actuable valve drive 54 has the transmission arrangement 35 and the gas exchange valve 26.
  • the transfer assembly 35 consists of a pivot lever assembly 56 and an intermediate lever assembly 58, wherein the intermediate lever assembly 58 via a working curve in Active connection with the pivot lever assembly 56 is, and wherein the pivot lever assembly 56 engages with an end face on the gas exchange valve 26 and the intermediate lever assembly 58 is in operative connection with the Ventilhubverstell responded 41 and the camshaft 40.
  • the Versteliorgan 48 of the Ventilhubverstell responded 41 engages against a biasing force of a spring 55 on a not further shown attack element (for example, a roller, see Figure 2) of the intermediate lever assembly 58 at.
  • the intermediate lever assembly 58 engages with a not shown in Figure 1 working curve 60 on the pivot lever assembly 56.
  • FIG. 2 now shows a schematic side view of an embodiment according to the invention a valve train assembly 10 for the gas exchange valve 26.
  • the camshaft 40 which is in operative connection with a first roller 62, on one of the working curve 60 of an intermediate lever 64 of the intermediate lever assembly 58 opposite end is rotatably mounted.
  • the intermediate lever 64 is further supported by a second roller 66 in a link 70.
  • a link 70 is in operative connection with two transmission arrangements. But it is of course also possible for each transmission arrangement to see a single backdrop 70 before.
  • the second roller 66 is shown in dashed lines in Figure 2, since it is covered by the first roller 62.
  • the working curve 60 of the intermediate lever 64 is in known manner with a roller 68 of the pivot lever 72 for the gas exchange valve 26 in operative connection.
  • a rotatably mounted in a bearing 84 adjusting lever 74 is provided on the first end 76, the control shaft 50 acts and the second end 78 with an attacking member 80 of Intermediate lever assembly 58 is operatively connected.
  • the engagement member 80 of the intermediate lever assembly 58 is formed by a surface portion 80 on the intermediate lever 64.
  • the adjusting lever 74 has a first rotatably mounted roller 82, which is in operative connection with this surface portion 80.
  • the adjusting lever 74 in the present case is also displaceably mounted in a bearing 84, which is indicated schematically by the double-sided arrow. Due to the slidable mounting of the control lever 74, a fine adjustment of the valve lifts can be made in a simple manner.
  • an intermediate lever assembly comprises two intermediate lever, which are connected via a connecting shaft in a known manner at the opposite end of the working curve.
  • first rollers for the power transmission of a camshaft are provided on the intermediate lever and a second roller, which is arranged between the intermediate levers and is provided for guidance in the backdrop.
  • the attacking member for the adjusting lever is advantageously formed by the connecting shaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention relates to a mechanically controllable valve drive arrangement (10) having a plurality of gas exchange valves (12, 14, 16, 18, 20, 22, 24, 26) disposed in a row, wherein a transmission arrangement (28, 29, 30, 31, 32, 33, 34, 35) is associated with a gas exchange valve (12, 14, 16, 18, 20, 22, 24, 26), wherein the transmission arrangement (28, 29, 30, 31, 32, 33, 34, 35) has at least one intermediate lever arrangement (58) and at least one pivot lever arrangement (56), wherein an intermediate lever (64) of the intermediate lever arrangement (58) has a working cam (60) for operatively connecting to a pivot lever (72) of the pivot lever arrangement (56), wherein the intermediate lever (64) is operatively connected to a peripheral contour of a camshaft (40) and wherein the intermediate lever arrangement (58) has an engagement element (80) which is operatively connected to a valve lift adjustment device (41), wherein the valve lift adjustment device (41) has a control shaft (50) which acts on a first end (76) of an adjusting lever (74), wherein the second end (78) is operatively connected to the engagement element (80) of the intermediate lever arrangement (58).

Description

B E S C H R E I B U N G  DESCRIPTION
Mechanisch steuerbare Ventiltriebanordnung Mechanically controllable valve train arrangement
Die Erfindung betrifft eine mechanisch steuerbare Ventiltriebanordnung mit mehreren in Reihe angeordneten Gaswechselventilen, denen entsprechende Zylinder zugeordnet sind, wobei einem Gaswechselventil eine Übertragungsanordnung zugeordnet ist, wobei die Übertragungsanordnung mindestens eine Zwischenhebelanordnung und mindestens eine Schwenkhebelanordnung aufweist, wobei ein Zwischenhebel der Zwischenhebelanordnung eine Arbeitskurve zur Wirkverbindung mit einem Schwenkhebel der Schwenkhebelanordnung aufweist, wobei der Zwischenhebel in Wirkverbindung mit einer Umfangskontur einer Nockenwelle steht und wobei die Zwischenhebelanordnung ein Angriffsorgan aufweist, das mit einer Ventilhubverstellung in Wirkverbindung steht. The invention relates to a mechanically controllable valve train arrangement having a plurality of gas exchange valves arranged in series, which are assigned to corresponding cylinders, wherein a gas exchange valve is assigned a transmission arrangement, wherein the transmission arrangement has at least one intermediate lever arrangement and at least one pivot lever arrangement, wherein an intermediate lever of the intermediate lever arrangement with a working curve for operative connection with a pivot lever of the pivot lever assembly, wherein the intermediate lever is operatively connected to a circumferential contour of a camshaft and wherein the intermediate lever assembly comprises an engaging member which is in operative connection with a valve lift.
Derartige Ventiltriebanordnungen sind hinlänglich bekannt. So beschreiben die DE 10 2006 033 559 AI und die DE 10 2007 022 266 AI Ventiltriebanordnungen, die eine einstellbare Hubhöhe eines betreffenden Gaswechselventils aufweisen. Hierzu ist in beiden Ventiltriebanordnungen eine Zwischenhebelanordnung vorgesehen, die einerseits mit einer Nockenwelle in Wirkverbindung steht, um das Gaswechselventil periodisch zu bewegen, und andererseits ein Angriffsorgan aufweist, über das die maximal bzw. minimal zu erreichende Hubhöhe einstellbar ist. All diese Ventiltriebanordnungen weisen jedoch den Nachteil auf, dass nach Fertigung und nachfolgender Montage aufgrund von Fertigungstoleranzen ein exakt gewünschter Ventilhub nicht einstellbar bzw. im Betriebszustand nicht wieder herstellbar ist. Insbesondere bei der Anforderung eines identischen Ventilhubs über alle Ventile und Zylinder eines Mehrzylinderverbrennungsmotors kann das bei geringen Ventilhüben zu einem unbefriedigenden Laufverhalten des Motors führen. Such valve train arrangements are well known. Thus, DE 10 2006 033 559 AI and DE 10 2007 022 266 AI valve train arrangements having an adjustable lift height of a gas exchange valve in question. For this purpose, an intermediate lever arrangement is provided in both valve train arrangements, which is on the one hand in operative connection with a camshaft to move the gas exchange valve periodically, and on the other hand has an attacking member, via which the maximum or minimum reachable lifting height is adjustable. However, all these valve train arrangements have the disadvantage that after production and subsequent assembly due to manufacturing tolerances a precisely desired valve lift is not adjustable or can not be restored in the operating state. Especially when requesting an identical valve lift across all valves and cylinders of a Multi-cylinder combustion engine can lead to unsatisfactory running behavior of the engine at low valve strokes.
Der Erfindung liegt daher die Aufgabe zugrunde, eine mechanisch steuerbare Ventiltriebanordnung derart auszugestalten, dass die oben beschriebenen Nachteile vermieden werden können. The invention is therefore based on the object to design a mechanically controllable valve train arrangement such that the disadvantages described above can be avoided.
Diese Aufgabe wird dadurch gelöst, dass die Ventilhubverstelleinrichtung eine Steuerwelle aufweist, die auf ein erstes Ende eines in einem Lager drehbar gelagerten Stellhebels einwirkt, wobei das zweite Ende mit dem Angriffsorgan der Zwischenhebelanordnung in Wirkverbindung steht. Über diesen sogenannten Stellhebel ist es auch im vormontierten oder endmontierten Zustand wesentlich einfacher, die Ventilhubhöhe des zugehörigen Gaswechselventils einzustellen. This object is achieved in that the Ventilhubverstelleinrichtung has a control shaft which acts on a first end of a rotatably mounted in a bearing actuating lever, wherein the second end is in operative connection with the engaging member of the intermediate lever assembly. About this so-called lever, it is much easier even in the preassembled or final assembled state to adjust the valve lift of the associated gas exchange valve.
Besonders vorteilhaft ist hier eine Ausführungsform, bei der der Stellhebel verschieblich angeordnet ist. Das Angriffsorgan der Zwischenhebelanordnung kann vorteilhaft durch einen Flächenabschnitt am Zwischenhebel gebildet sein, wobei in vorteilhafter Weise der Stellhebel eine erste drehbar gelagerte Rolle aufweist, die mit dem Flächenabschnitt des Zwischenhebels in Wirkverbindung stehen kann. Durch diese Anordnung wird eine wesentlich geringere Flächenpressung erreicht als mit den konventionellen Anordnungen. Particularly advantageous here is an embodiment in which the adjusting lever is arranged displaceably. The engagement member of the intermediate lever assembly may advantageously be formed by a surface portion on the intermediate lever, wherein advantageously the adjusting lever has a first rotatably mounted roller, which may be in operative connection with the surface portion of the intermediate lever. By this arrangement, a substantially lower surface pressure is achieved than with the conventional arrangements.
Auch kann der Zwischenhebel in vorteilhafter Weise eine zweite drehbar gelagerte Rolle aufweisen, die mit der Steuerwelle in Wirkverbindung steht, um Verschleißerscheinungen noch weiter zu minimieren. Also, the intermediate lever may advantageously have a second rotatably mounted roller, which is in operative connection with the control shaft to further minimize wear phenomena.
Vorteilhafter Weise weist der Zwischenhebel an dem der Arbeitskontur entgegen gesetzten Seite eine erste Rolle aufweist, die in Wirkverbindung mit der Nockenwelle steht, und eine zweite Rolle aufweist, die in einer Kulisse geführt ist, wobei das Angriffsorgan zwischen der ersten Rolle und der Arbeitskontur vorgesehen ist. Advantageously, the intermediate lever on the working contour opposite side has a first roller, which is in operative connection with the camshaft, and has a second roller which in a Setting is performed, the attacking member is provided between the first roller and the working contour.
In einer besonders vorteilhaften Ausführungsform ist es darüber hinaus möglich, dass eine Zwischenhebelanordnung zwei Zwischenhebel aufweist, die über eine Verbindungswelle an dem der Arbeitskurve entgegengesetzten Ende miteinander verbunden sind, wobei erste Rollen für die Kraftübertragung einer Nockenwelle auf die Zwischenhebel vorgesehen sind und eine zweite Rolle zwischen den Zwischenhebeln zur Führung in einer Kulisse vorgesehen ist, wobei das Angriffsorgan durch die Verbindungsweife ausgebildet ist. In a particularly advantageous embodiment, it is also possible that an intermediate lever assembly comprises two intermediate levers, which are connected via a connecting shaft at the opposite end of the working curve, wherein first rollers are provided for the transmission of a camshaft to the intermediate lever and a second roller between the intermediate levers is provided for guidance in a backdrop, wherein the attacking member is formed by the Verbindungsweife.
Die Erfindung wird nachfolgend anhand der Zeichnung näher erläutert, hierin zeigen : The invention will be explained in more detail below with reference to the drawing, in which:
Figur 1 eine perspektivische Darstellung einer erfinderischen Ventiltriebanordnung, die nach dem Grundprinzip„Univalve" funktioniert, und Figure 1 is a perspective view of an inventive valve train assembly that works on the basic principle "Univalve", and
Figur 2 eine schematische Seitenansicht einer erfindungsgemäßen Ausführungsform einer Ventiltriebanordnung für ein Gaswechselventil. Figure 2 is a schematic side view of an embodiment according to the invention of a valve train assembly for a gas exchange valve.
Figur 1 zeigt eine Ausführungsform einer erfindungsgemäßen Ventiltriebanordnung 10 mit mehreren in Reihe angeordneten Gaswechselventilen 12, 14, 16, 18, 20, 22, 24 und 26. Im vorliegenden Fall sind jeweils zwei Einlass-Gaswechselventile einem Zylinder der Brennkraftmaschine zugeordnet Die mechanisch steuerbare Ventiltriebanordnung 10 weist im vorliegenden Fall vier Übertragungsanordnungen 28, 29, 30, 31, 32, 33 und 34, 35 auf, denen jeweils zwei Gaswechselventile 12, 14; 16, 18; 20, 22; 24, 26 zugeordnet sind. Dabei sind die Übertragungsanordnungen 28, 29, 30, 31, 32, 33 und 34, 35 auf bekannte Weise im Zylinderkopf mittels Lagermitteln gelagert. Die Lagermittel 36, 38 werden in der vorliegenden Figur 1 lediglich exemplarisch für die Lagerung eines Schwenkhebels 56 der Übertragungsanordnung 35 dargestellt. Darüber hinaus stehen die Übertragungsanordnungen 28, 29, 30, 31, 32, 33 und 34, 35 auf bekannte Weise mit einer Nockenwelle 40 in Wirkverbindung. Außerdem ist jede Übertragungsanordnung 28, 29, 30, 31, 32, 33 und 34, 35 durch Verstellorgane 42, 43, 44, 45, 46, 47 und 48, 49 einer Ventifhubverstelleinrichtung 41 derart ansteuerbar, dass ein geringerer oder höherer Ventilhub der Einlassventile 12, 14, 16, 18, 20, 22, 24, 26 einstellbar ist. Im vorliegenden Ausführungsbeispiel sind die Verstellorgane 42, 43, 44, 45, 46, 47 und 48, 49 jeweils zwei Einlassventilen 12, 14; 16, 18; 20, 22; 24, 26 zugeordnet und als Steuerorgane ausgeführt, die auf einer Steuerweile 50 vorgesehen sind und auf Angriffsorgane 75 einwirken. Die Steuerwelle 50 ist hier als Exzenterwelle ausgeführt. Es sollte deutlich sein, dass die Steuerwelle 50 jegliche Art von Ansteuerkonturen aufweisen kann. Die Ventilhubversteileinrichtung 41 ist im vorliegenden Ausführungsbeispiel durch ein Antriebsorgan 52 auf bekannte Weise antreibbar. Es ist natürlich auch möglich mehreren Gaswechselventilen eine Übertragungsanordnung zuzuordnen. Als Antriebsorgan 52 kann ein sowohl vorwärts wie rückwärts laufender Drehantrieb genutzt werden. Die Ventilhubversteileinrichtung 41 kann damit derart angetrieben werden, dass in Abhängigkeit von der vorliegenden Position schnell und präzise der dem nächsten Betriebszustand entsprechende Ventilhub durch den Einsatz der entsprechenden Steuerorgane gewählt werden kann. Auch Drehwinkel von > 360° sind damit realisierbar. 1 shows an embodiment of a valve train arrangement 10 according to the invention with a plurality of gas exchange valves 12, 14, 16, 18, 20, 22, 24 and 26 arranged in series. In the present case, two inlet gas exchange valves are assigned to one cylinder of the internal combustion engine. The mechanically controllable valve train arrangement 10 has in the present case four transmission arrangements 28, 29, 30, 31, 32, 33 and 34, 35, which in each case two gas exchange valves 12, 14; 16, 18; 20, 22; 24, 26 are assigned. The transmission arrangements 28, 29, 30, 31, 32, 33 and 34, 35 are mounted in a known manner in the cylinder head by means of bearing means. The bearing means 36, 38 are shown in the present figure, only by way of example for the storage of a pivot lever 56 of the transfer assembly 35. In addition, the transmission assemblies 28, 29, 30, 31, 32, 33 and 34, 35 in known manner with a camshaft 40 in operative connection. In addition, each transmission assembly 28, 29, 30, 31, 32, 33 and 34, 35 by adjusting members 42, 43, 44, 45, 46, 47 and 48, 49 of a Ventifhubverstelleinrichtung 41 can be controlled such that a lesser or higher valve lift of the intake valves 12, 14, 16, 18, 20, 22, 24, 26 is adjustable. In the present embodiment, the adjusting members 42, 43, 44, 45, 46, 47 and 48, 49 are each two inlet valves 12, 14; 16, 18; 20, 22; Assigned 24, 26 and executed as control organs, which are provided on a Steuerweile 50 and act on attack elements 75. The control shaft 50 is designed here as an eccentric shaft. It should be understood that the control shaft 50 may have any type of drive contours. The Ventilhubversteileinrichtung 41 is driven in the present embodiment by a drive member 52 in a known manner. Of course, it is also possible to assign several gas exchange valves to a transmission arrangement. As a drive member 52, both a forward and reverse running rotary drive can be used. The Ventilhubversteileinrichtung 41 can thus be driven in such a way that depending on the present position quickly and precisely the valve operating stroke corresponding to the next operating state can be selected by the use of the corresponding control elements. Even angles of rotation of> 360 ° can be realized.
Im vorliegenden Ausführungsbeispiel weist ein mechanisch ansteuerbarer Ventiltrieb 54 die Übertragungsanordnung 35 sowie das Gaswechselventil 26 auf. Die Übertragungsanordnung 35 besteht dabei aus einer Schwenkhebelanordnung 56 sowie einer Zwischenhebelanordnung 58, wobei die Zwischenhebelanordnung 58 über eine Arbeitskurve in Wirkverbindung mit der Schwenkhebelanordnung 56 steht, und wobei die Schwenkhebelanordnung 56 mit einer Stirnfläche auf das Gaswechselventil 26 angreift und die Zwischenhebelanordnung 58 in Wirkverbindung mit der Ventilhubverstelleinrichtung 41 und der Nockenwelle 40 steht. Dabei greift das Versteliorgan 48 der Ventilhubverstelleinrichtung 41 entgegen einer Vorspannkraft einer Feder 55 auf ein nicht weiter dargestelltes Angriffsorgan (beispielsweise eine Rolle, siehe Figur 2) der Zwischenhebelanordnung 58 an. Die Zwischenhebelanordnung 58 greift mit einer in Figur 1 nicht weiter dargestellten Arbeitskurve 60 auf die Schwenkhebelanordnung 56 an. In the present exemplary embodiment, a mechanically actuable valve drive 54 has the transmission arrangement 35 and the gas exchange valve 26. The transfer assembly 35 consists of a pivot lever assembly 56 and an intermediate lever assembly 58, wherein the intermediate lever assembly 58 via a working curve in Active connection with the pivot lever assembly 56 is, and wherein the pivot lever assembly 56 engages with an end face on the gas exchange valve 26 and the intermediate lever assembly 58 is in operative connection with the Ventilhubverstelleinrichtung 41 and the camshaft 40. In this case, the Versteliorgan 48 of the Ventilhubverstelleinrichtung 41 engages against a biasing force of a spring 55 on a not further shown attack element (for example, a roller, see Figure 2) of the intermediate lever assembly 58 at. The intermediate lever assembly 58 engages with a not shown in Figure 1 working curve 60 on the pivot lever assembly 56.
Figur 2 zeigt nun eine schematische Seitenansicht einer erfindungsgemäßen Ausführungsform einer Ventiltriebanordnung 10 für das Gaswechselventil 26. Deutlich zu erkennen ist die Nockenwelle 40, die in Wirkverbindung mit einer ersten Rolle 62 steht, die an einem der Arbeitskurve 60 eines Zwischenhebels 64 der Zwischenhebelanordnung 58 entgegengesetzten Ende drehbar gelagert ist. Durch die Nockenwelle 40 wird gegen den unter Vorspannkraft einer nicht dargestellten Feder stehenden Zwischenhebefs 64 die Hubbewegung des Gaswechselventils 26 ausgelöst. Der Zwischenhebel 64 ist des Weiteren über eine zweite Rolle 66 in einer Kulisse 70 gelagert. Gemäß Figur 1 steht im vorliegenden Ausführungsbeispiel eine Kulisse 70 in Wirkverbindung mit zwei Übertragungsanordnungen. Es ist aber natürlich auch möglich für jede Übertragungsanordnung eine einzelne Kulisse 70 vor zu sehen. Die zweite Rolle 66 ist jedoch in der Figur 2 nur gestrichelt dargestellt, da sie durch die erste Rolle 62 verdeckt ist. Die Arbeitskurve 60 des Zwischenhebels 64 steht auf bekannte Weise mit einer Rolle 68 des Schwenkhebels 72 für das Gaswechselventil 26 in Wirkverbindung. Gegenüber dem Stand der Technik, bei dem ein Verstellorgan direkt ein Angriffsorgan des Zwischenhebels angreift, ist nun ein in einem Lager 84 drehbar gelagerter Stellhebel 74 vorgesehen, auf dessen erstes Ende 76 die Steuerwelle 50 einwirkt und dessen zweites Ende 78 mit einem Angriffsorgan 80 der Zwischenhebelanordnung 58 in Wirkverbindung steht. Im vorliegenden Ausführungsbeispiel ist das Angriffsorgan 80 der Zwischenhebelanordnung 58 durch einen Flächenabschnitt 80 am Zwischenhebel 64 ausgebildet. Des Weiteren weist der Stellhebel 74 eine erste drehbar gelagerte Rolle 82 auf, die mit diesem Flächenabschnitt 80 in Wirkverbindung steht. Durch eine derartige Ausführungsform, die eine Auslagerung der Steuerwellenkontaktrolle als Angriffsorgan aus dem Zwischenhebel 64 heraus bewirkt, verringert sich die Masse und somit das Massenträgheitsmoment des Zwischenhebels 64. Dies bewirkt eine höhere Drehzahlfestigkeit des Systems. Darüber hinaus treten bei der Ventiltriebanordnung gemäß dem Stand der Technik zwischen der Steuerwelle und dem Angriffsorgan hohe Flächenpressungen auf. Bei der hier dargestellten Lösung ist dieser Kontakt ersetzt durch zwei Kontakte, nämlich einmal der Kontakt zwischen Steuerwelle 50 und Stellhebel 74 und des Weiteren durch den Kontakt der ersten Rolle 82 des Stellhebels 74 mit dem Flächenabschnitt 80 des Zwischenhebels 64. Hierdurch ergeben sich wesentlich geringere Flächenpressungen. Figure 2 now shows a schematic side view of an embodiment according to the invention a valve train assembly 10 for the gas exchange valve 26. Clearly visible is the camshaft 40, which is in operative connection with a first roller 62, on one of the working curve 60 of an intermediate lever 64 of the intermediate lever assembly 58 opposite end is rotatably mounted. By the camshaft 40, the lifting movement of the gas exchange valve 26 is triggered against the under biasing force of a spring, not shown, Zwischenhebefs 64. The intermediate lever 64 is further supported by a second roller 66 in a link 70. According to FIG. 1, in the present exemplary embodiment, a link 70 is in operative connection with two transmission arrangements. But it is of course also possible for each transmission arrangement to see a single backdrop 70 before. However, the second roller 66 is shown in dashed lines in Figure 2, since it is covered by the first roller 62. The working curve 60 of the intermediate lever 64 is in known manner with a roller 68 of the pivot lever 72 for the gas exchange valve 26 in operative connection. Compared to the prior art, in which an adjusting directly engages an attack organ of the intermediate lever, now a rotatably mounted in a bearing 84 adjusting lever 74 is provided on the first end 76, the control shaft 50 acts and the second end 78 with an attacking member 80 of Intermediate lever assembly 58 is operatively connected. In the present embodiment, the engagement member 80 of the intermediate lever assembly 58 is formed by a surface portion 80 on the intermediate lever 64. Furthermore, the adjusting lever 74 has a first rotatably mounted roller 82, which is in operative connection with this surface portion 80. By such an embodiment, which causes a removal of the control shaft contact roller as an attack organ from the intermediate lever 64, the mass and thus the moment of inertia of the intermediate lever 64 is reduced. This causes a higher speed stability of the system. In addition, occur in the valve train assembly according to the prior art between the control shaft and the attack high surface pressures. In the solution shown here, this contact is replaced by two contacts, namely once the contact between the control shaft 50 and lever 74 and further by the contact of the first roller 82 of the actuating lever 74 with the surface portion 80 of the intermediate lever 64. This results in much lower surface pressures ,
Des Weiteren ist der Stellhebel 74 im vorliegenden Fall auch noch in einem Lager 84 verschieblich gelagert, was schematisch durch den doppelseitigen Pfeil angedeutet ist. Aufgrund der verschieblichen Lagerung des Stellhebels 74 kann auf einfache Weise eine Feineinstellung der Ventilhübe vorgenommen werden. Furthermore, the adjusting lever 74 in the present case is also displaceably mounted in a bearing 84, which is indicated schematically by the double-sided arrow. Due to the slidable mounting of the control lever 74, a fine adjustment of the valve lifts can be made in a simple manner.
Natürlich ist es auch möglich, dass in einem weiteren Ausführungsbeispiel eine Zwischenhebelanordnung zwei Zwischenhebel aufweist, die über eine Verbindungswelle auf bekannte Weise an dem der Arbeitskurve entgegengesetzten Ende miteinander verbunden sind. Hierbei sind erste Rollen für die Kraftübertragung einer Nockenwelle auf die Zwischenhebel vorgesehen und eine zweite Rolle, die zwischen den Zwischenhebeln angeordnet ist und zur Führung in der Kulisse vorgesehen ist. In diesem Fall wird das Angriffsorgan für den Stellhebel vorteilhafter Weise durch die Verbindungswelle ausgebildet. Of course, it is also possible that in a further embodiment, an intermediate lever assembly comprises two intermediate lever, which are connected via a connecting shaft in a known manner at the opposite end of the working curve. In this case, first rollers for the power transmission of a camshaft are provided on the intermediate lever and a second roller, which is arranged between the intermediate levers and is provided for guidance in the backdrop. In this Case, the attacking member for the adjusting lever is advantageously formed by the connecting shaft.

Claims

P A T E N T A N S P R Ü C H E PATENT APPLICATIONS
1. Mechanisch steuerbare Ventiltriebanordnung (10) mit mehreren in Reihe angeordneten Gaswechselventilen (12, 14, 16, 18, 20, 22, 24, 26), denen entsprechende Zylinder zugeordnet sind, wobei einem Gaswechselventil (12, 14, 16, 18, 20, 22, 24, 26) eine Übertragungsanordnung (28, 29, 30, 31, 32, 33, 34, 35) zugeordnet ist, wobei die Übertragungsanordnung (28, 29, 30, 31, 32, 33, 34, 35) mindestens eine Zwischenhebelanordnung (58) und mindestens eine Schwenkhebelanordnung (56) aufweist, wobei ein Zwischenhebel (64) der Zwischenhebelanordnung (58) eine Arbeitskurve (60) zur Wirkverbindung mit einem Schwenkhebel (72) der Schwenkhebelanordnung (56) aufweist, wobei der Zwischenhebel (64) in Wirkverbindung mit einer Umfangskontur einer Nockenwelle (40) steht und wobei die Zwischenhebelanordnung (58) ein Angriffsorgan (80) aufweist, das mit einer Ventilhubverstelleinrichtung (41) in Wirkverbindung steht, dadurch gekennzeichnet, dass die Ventilhubverstelleinrtchtung (41) eine Steuerwelle (50) aufweist, die auf ein erstes Ende (76) eines in einem Lager (84) drehbar gelagerten Stellhebels (74) einwirkt, wobei das zweite Ende (78) mit dem Angriffsorgan (80) der Zwischenhebelanordnung (58) in Wirkverbindung steht. 1. Mechanically controllable valve train arrangement (10) with a plurality of gas exchange valves arranged in series (12, 14, 16, 18, 20, 22, 24, 26) to which corresponding cylinders are assigned, wherein a gas exchange valve (12, 14, 16, 18, 20, 22, 24, 26) is associated with a transmission arrangement (28, 29, 30, 31, 32, 33, 34, 35), wherein the transmission arrangement (28, 29, 30, 31, 32, 33, 34, 35) at least one intermediate lever arrangement (58) and at least one pivot lever arrangement (56), wherein an intermediate lever (64) of the intermediate lever arrangement (58) has a working cam (60) for operative connection with a pivot lever (72) of the pivot lever arrangement (56), wherein the intermediate lever ( 64) is in operative connection with a peripheral contour of a camshaft (40) and wherein the intermediate lever arrangement (58) has an engagement member (80) which is in operative connection with a valve lift adjusting device (41), characterized in that the valve lift adjustment device (41) comprises a control shaft (40). 50) which acts on a first end (76) of a bearing (84) rotatably mounted adjusting lever (74), wherein the second end (78) with the engaging member (80) of the intermediate lever assembly (58) is in operative connection.
Mechanisch steuerbare Ventiltriebanordnung nach Anspruch 1, dadurch gekennzeichnet, dass der Stellhebel (74) verschieblich angeordnet ist. Mechanically controllable valve drive arrangement according to claim 1, characterized in that the adjusting lever (74) is arranged displaceably.
Mechanisch steuerbare Ventiltriebanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Angriffsorgan (80) der Zwischenhebelanordnung (58) durch einen Flächenabschnitt am Zwischenhebel (64) gebildet ist. Mechanically controllable valve train arrangement according to claim 1 or 2, characterized in that the engagement member (80) of the intermediate lever assembly (58) by a surface portion on the intermediate lever (64) is formed.
4. Mechanisch steuerbare Ventiltriebanordnung nach Anspruch 3, dadurch gekennzeichnet, dass das der Stellhebel (74) eine erste drehbar gelagerte Rolle (82) aufweist, die mit dem Flächenabschnitt (80) des Zwischenhebels (64) in Wirkverbindung steht. 4. Mechanically controllable valve train assembly according to claim 3, characterized in that the adjusting lever (74) has a first rotatably mounted roller (82) which is in operative connection with the surface portion (80) of the intermediate lever (64).
5. Mechanisch steuerbare Ventiltriebanordnung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass das der5. Mechanically controllable valve train arrangement according to one of the preceding claims, characterized in that the
Zwischenhebel (64) eine zweite drehbar gelagerte Rolle aufweist, die mit der Steuerwelle (50) in Wirkverbindung steht. Intermediate lever (64) has a second rotatably mounted roller which is in operative connection with the control shaft (50).
6. Mechanisch steuerbare Ventiltriebanordnung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass der6. Mechanically controllable valve train arrangement according to one of the preceding claims, characterized in that the
Zwischenhebel (64) an dem der Arbeitskontur (60) entgegen gesetzten Seite eine erste Rolle (62) aufweist, die in Wirkverbindung mit der Nockenwelle (40) steht, und eine zweite Rolle (66) aufweist, die in einer Kulisse (70) geführt ist, wobei das Angriffsorgan (80) zwischen der ersten Rolle (62) und der Arbeitskontur (60) vorgesehen ist. Intermediate lever (64) on the working contour (60) opposite side has a first roller (62) which is in operative connection with the camshaft (40), and a second roller (66) which guided in a link (70) is, wherein the engagement member (80) between the first roller (62) and the working contour (60) is provided.
7. Mechanisch steuerbare Ventiltriebanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass eine Zwischenhebelanordnung (58) zwei Zwischenhebel aufweist, die über eine Verbindungswelle an dem der Arbeitskurve (60) entgegen gesetzten Ende miteinander verbunden sind, wobei erste Rollen für die Kraftübertragung einer Nockenwelle (40) auf die Zwischenhebel vorgesehen sind und eine zweite Rolle zwischen den Zwischenhebeln zur Führung in einer Kulisse (70) vorgesehen ist, wobei das Angriffsorgan durch die Verbindungswelle ausgebildet ist. 7. Mechanically controllable valve train assembly according to claim 1 or 2, characterized in that an intermediate lever assembly (58) has two intermediate lever, which are connected via a connecting shaft at the working curve (60) opposite end, wherein first rollers for the transmission of a camshaft (40) are provided on the intermediate lever and a second roller between the intermediate levers for guiding in a link (70) is provided, wherein the engagement member is formed by the connecting shaft.
EP12809746.6A 2012-03-08 2012-12-17 Mechanical valve drive Active EP2823158B1 (en)

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PCT/EP2012/075788 WO2013131593A1 (en) 2012-03-08 2012-12-17 Mechanically controllable valve drive arrangement

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DE102012004413B4 (en) 2016-05-25
US20150027392A1 (en) 2015-01-29
US9206716B2 (en) 2015-12-08
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ES2553464T3 (en) 2015-12-09
CN104105849A (en) 2014-10-15

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