EP1458956A1 - Device for variable actuation of the gas exchange valves in internal combustion piston engines - Google Patents

Device for variable actuation of the gas exchange valves in internal combustion piston engines

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Publication number
EP1458956A1
EP1458956A1 EP02799032A EP02799032A EP1458956A1 EP 1458956 A1 EP1458956 A1 EP 1458956A1 EP 02799032 A EP02799032 A EP 02799032A EP 02799032 A EP02799032 A EP 02799032A EP 1458956 A1 EP1458956 A1 EP 1458956A1
Authority
EP
European Patent Office
Prior art keywords
intermediate member
housing
joint
curve
cam
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
EP02799032A
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German (de)
French (fr)
Other versions
EP1458956B1 (en
Inventor
Helmut Schön
Peter Kuhn
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Fraunhofer Gesellschaft zur Forderung der Angewandten Forschung eV
Original Assignee
Fraunhofer Gesellschaft zur Forderung der Angewandten Forschung eV
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Publication of EP1458956A1 publication Critical patent/EP1458956A1/en
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Publication of EP1458956B1 publication Critical patent/EP1458956B1/en
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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

Definitions

  • the invention specified in claim 1 is based on the object, the requirements placed on the engine by a variable
  • Valve control better than the state of the art. These requirements are described on the one hand in the design of the individual valve lift profiles, the family of valve lift profiles that can be generated and on the other hand in the size of the mechanical losses due to friction when driving the valves.
  • the individual valve lift profiles and the family of valve lift profiles that can be generated must be as free as possible with regard to Opening angle, closing angle, valve lift, valve acceleration curve and phase position to the crank angle can be designed.
  • the losses due to mechanical friction should be kept as small as possible. As far as possible, these requirements are to be met without additional construction effort, in particular construction height.
  • the gearbox consists of a driving shaft (W), which is guided in a rotatable joint (wg) in the housing (G) and which actuates an intermediate link (Z) via a cam joint (zw).
  • This intermediate link (Z) is supported on the one hand via a cam joint (zg) in the housing (G), for example in the cylinder head, and is operatively connected to an output link (A).
  • the cam joint (zg) between the intermediate member (Z) and the housing (G) consists of a section forming a catch and a control section. To change the valve stroke, it is provided that the position (a) of the control section relative to the swivel joint (wg) of the shaft (W) in the housing (G) can be changed during engine operation.
  • the output member (A) is clearly in the housing (G), for example in a swivel joint (ag) and transmits the movement to at least one valve (V).
  • the advantages achieved with the invention result from the fact that the intermediate member (Z) is connected to the output member (A) via a cam joint (za) and thereby the number of joint values on the intermediate member (Z) driven by the shaft (W) and at the same time the sum of the joint valency of the transmission is reduced.
  • the transmission has an additional degree of freedom of movement, which involves a displacement of the intermediate link (Z) relative to the abrasion link (A) along the curve of the cam joint (za) between the intermediate link (Z) and the output link (A) and at the same time a rotation of the intermediate link (Z) relative to the abrasion member (A) around that
  • the additional degree of freedom of movement causes the intermediate link (Z) to roll off the output link (A).
  • This rotary movement causes a displacement flow of the lubricant, which in turn significantly supports the build-up of a load-bearing lubricating film in the contact between the intermediate link (Z) and the output link (A).
  • the rotary movement partially reduces the sliding speed at the contact point by rolling. Each of these effects reduces the friction at the contact point mentioned.
  • the design according to the invention also has the advantage of not requiring more space than in the prior art.
  • the advantageous design of the contour (Kaz or / and Kza) of at least one of the two contact partners in the curved joint (za) between the intermediate member (Z) and the output member (A) is described as a circular arc.
  • the contour determining the curve joint is assigned exclusively to one contact partner
  • the contour of the other contact partner becomes an arc or a circle, which is advantageously designed as a rotatable roller.
  • the contact partners roll on the shape determining the cam joint and the tangential movement is shifted onto the bearing of the rotatable roller. Due to the materials and lubrication conditions known from plain bearings and the use of a small friction radius, the friction in this cam joint is reduced.
  • Claim 4 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zg) between the intermediate member (Z) and housing (G) is formed exclusively by the contour (Kzul) on the intermediate member (Z) and the contour (Kgzl) of the housing Support is a fit role ( Figure 2).
  • Claim 5 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zg) between the intermediate member (Z) and the housing (G) is formed exclusively by the contour (Kgz2) on the housing (G) and the intermediate-side contour (Kzg2) is one viable role is (Figure 3).
  • Claim 6 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zw) between the intermediate member (Z) and the shaft (W) is formed exclusively by the contour (Kwzl) on the shaft (W) and the link-side contour (Kzwl) is a fit role (Figure 4).
  • Claim 7 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (za) between the intermediate element (Z) and the output element (A) is formed exclusively by the contour (Kazl) on the output element (A) and the intermediate element-side contour (Kzal) Circular arc ( Figure 5) or a fit Rolie.
  • Claim 10 describes the advantageous design of the intermediate member (Z), in which at least two of the curved joints on the intermediate member (Z) are represented on the intermediate member side by rotating bodies and at least two of the centers of rotation of these rotating bodies coincide. In this way, the installation space is minimized and the forces resulting from the rotational acceleration of the intermediate member (Z) are reduced.
  • Claim 11 is carried out that by a joint actuation of several output members (Ai) and valves (Vi) of a cylinder by a cam (N) and an intermediate member (Z), the number of joints and the moving masses can be reduced, which is advantageous Reduced friction and, by reducing the number of components, also reduced the construction effort (Figure 7).
  • the part (g2) forming the control area can be rotatably mounted in a sliding part (S) and the sliding part (S) can be slidably mounted in the housing (G).
  • the displacement position (rs) of the sliding part (S) can be set, for example, by a cam (VNs) fastened in the housing (G).
  • Rotational movement (rd) of the part (g2) forming the control area can be adjusted by a cam (VNd) fastened in the housing (G) or by a cam (VNd) fastened in the slant part (S).
  • the rotary movement (rd) of the part (g2) forming the control area can be set independently of the displacement position (rs) of the sliding part (S).
  • the rotary movement (rd) is controlled by a cam in the housing (G) by the displacement (rs) of the sliding part (S).
  • the position (a) of the control curve can be displaced (rv) and rotated (rd) in the latching direction. This further increases the design freedom of the valve lift curve. A loss of contact of the transmission members does not occur.
  • the valve acceleration and valve lift can also be changed ( Figure 8).
  • the part (gl) forming the latching section in the housing (G) can be used to ensure the return movement of the intermediate link (Z) and thus the cam contact by being rotatably mounted in the housing (G) and exerting a force on the intermediate link (Z) exercises which moves this towards the cam (N).
  • This force is generated, for example, via a spring force (KF).
  • KF spring force

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

Abstract

The invention relates to a revolving gear consisting of a housing (G), a shaft (W), an intermediate member (Z) and an output member (A). The shaft is revolvably guided in the housing in a rotating joint (wb) and actuates the intermediate member by means of a curved joint (zw). The intermediate member is supported by a curved joint (zg) in the housing and is actively connected to the output member by another curved joint (za). The curved joint between the intermediate member and the housing has a controlling section enabling movement to be transmitted to the output member and a locking section preventing movement from being transmitted to the output member. The output member is unequivocally guided in the housing and transmits movement to at least one valve (V).

Description

Beschreibungdescription
Vorrichtung zur variablen Betätigung der Ladungswechselventile in HubkolbenmotorenDevice for variable actuation of the charge exchange valves in reciprocating engines
Es ist bekannt, daß der Hubverlauf der Ladungswechselventile in Hubkolbenmotoren einen entscheidenden Einfluß auf das Betriebsverhalten und die Betriebswerte des Motors hat. Insbesondere zur Verminderung der Ladungswechselverluste bei ladungsmassengesteuerten Motoren ist ein im Motorbetrieb kontinuierlich veränderbarer Ventilhubverlauf wünschenswert. Dabei kann sowohl eine Veränderung des Hubverlaufs von Ein- und Auslaßventilen, als auch eine Veränderung nur bei den Einlaßventilen vorteilhaft sein. Für die technische Umsetzung einer solchen variablen Ventilsteuerung sind u.a. viergliedrige Ventilgetriebe (z.B. DE 38 33 540 C2, DE 43 22 449 AI, BMW-valvetronic) bekannt. Solche Ventilgetriebe ermöglichen eine kontinuierliche Veränderung des Ventilhubverlaufs im Motorbetrieb.It is known that the stroke course of the charge exchange valves in reciprocating piston engines has a decisive influence on the operating behavior and the operating values of the engine. In particular, in order to reduce the charge change losses in charge-mass-controlled engines, a valve lift curve that is continuously variable during engine operation is desirable. Both a change in the stroke profile of intake and exhaust valves and a change only in the intake valves can be advantageous. For the technical implementation of such a variable valve control, four-link valve transmission (e.g. DE 38 33 540 C2, DE 43 22 449 AI, BMW-valvetronic) known. Such valve gears enable a continuous change in the course of the valve stroke during engine operation.
Der im Patentanspruch 1 angegebenen Erfindung liegt die Aufgabe zugrunde, die vom Motor gestellten Anforderungen an eine variableThe invention specified in claim 1 is based on the object, the requirements placed on the engine by a variable
Ventilsteuerung besser als nach dem Stand der Technik zu erfüllen. Diese Anforderungen beschreiben sich zum einen in der Gestaltung der einzelnen Ventilhubverläufe, der erzeugbaren Schar an Ventilhubverläufen und zum anderen in der Größe der mechanischen Verluste durch Reibung beim Antrieb der Ventile. Die einzelnen Ventilhubverläufe und die erzeugbare Schar an Ventilhubverläufen müssen möglichst frei hinsichtlich Öffnungswinkel, Schließwinkel, Ventilhub, Ventilbeschleunigungsverlauf und Phasenlage zum Kurbelwinkel gestaltbar sein. Die Verluste durch mechanische Reibung sind möglichst klein zu halten. Diese Anforderungen sind möglichst ohne zusätzlichen Bauaufwand, insbesondere Bauhöhe zu erfüllen.Valve control better than the state of the art. These requirements are described on the one hand in the design of the individual valve lift profiles, the family of valve lift profiles that can be generated and on the other hand in the size of the mechanical losses due to friction when driving the valves. The individual valve lift profiles and the family of valve lift profiles that can be generated must be as free as possible with regard to Opening angle, closing angle, valve lift, valve acceleration curve and phase position to the crank angle can be designed. The losses due to mechanical friction should be kept as small as possible. As far as possible, these requirements are to be met without additional construction effort, in particular construction height.
Die Aufgabe wird durch die im Patentanspruch 1 aufgeführten Merkmale eines Getriebes zur Betätigung der Ventile gelöst.The object is achieved by the features of a transmission for actuating the valves listed in claim 1.
Das Getriebe besteht aus einer antreibenden Welle (W), welche im Gehäuse (G) in einem Drehgelenk (wg) umlauffähig geführt ist und welche über ein Kurvengelenk (zw) ein Zwischenglied (Z) betätigt. Dieses Zwischenglied (Z) stützt sich zum einen über ein Kurvengelenk (zg) im Gehäuse (G), zum Beispiel im Zylinderkopf ab und ist mit einem Abtriebsglied (A) wirkverbunden. Das Kurvengelenk (zg) zwischen dem Zwischenglied (Z) und dem Gehäuse (G) besteht aus einem eine Rast bildenden Abschnitt und aus einem Steuerabschnitt. Zur Veränderung des Ventilhubes ist vorgesehen, die Position (a) des Steuerabschnittes zum Drehgelenk (wg) der Welle (W) im Gehäuse (G) im Motorbetrieb veränderbar zu gestalten. Das Abtriebsglied (A) ist im Gehäuse (G) eindeutig, beispielsweise in einem Drehgelenk (ag) geführt und überträgt die Bewegung auf mindestens ein Ventil (V).The gearbox consists of a driving shaft (W), which is guided in a rotatable joint (wg) in the housing (G) and which actuates an intermediate link (Z) via a cam joint (zw). This intermediate link (Z) is supported on the one hand via a cam joint (zg) in the housing (G), for example in the cylinder head, and is operatively connected to an output link (A). The cam joint (zg) between the intermediate member (Z) and the housing (G) consists of a section forming a catch and a control section. To change the valve stroke, it is provided that the position (a) of the control section relative to the swivel joint (wg) of the shaft (W) in the housing (G) can be changed during engine operation. The output member (A) is clearly in the housing (G), for example in a swivel joint (ag) and transmits the movement to at least one valve (V).
Die mit der Erfindung erzielten Vorteile ergeben sich daraus, daß das Zwischenglied (Z) mit dem Abtriebsglied (A) über ein Kurvengelenk (za) verbunden ist und hierdurch die Zahl der Gelenkwertigkeiten an dem von der Welle (W) angetriebenen Zwischenglied (Z) und gleichzeitig die Summe der Gelenkwertigkeiten des Getriebes vermindert wird. Im Gegensatz zu dem bekannten Stand der Technik hat das Getriebe einen zusätzlichen Bewegungsfreiheitsgrad, welcher eine Verschiebung des Zwischengliedes (Z) relativ zum Abriebsglied (A) entlang der Kurve des Kurvengelenkes (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) und gleichzeitig eine Drehung des Zwischengliedes (Z) relativ zum Abriebsglied (A) um dasThe advantages achieved with the invention result from the fact that the intermediate member (Z) is connected to the output member (A) via a cam joint (za) and thereby the number of joint values on the intermediate member (Z) driven by the shaft (W) and at the same time the sum of the joint valency of the transmission is reduced. In contrast to In the known state of the art, the transmission has an additional degree of freedom of movement, which involves a displacement of the intermediate link (Z) relative to the abrasion link (A) along the curve of the cam joint (za) between the intermediate link (Z) and the output link (A) and at the same time a rotation of the intermediate link (Z) relative to the abrasion member (A) around that
Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) zulässt. Mit dem erfindungsgemäßen Kurvengelenk (za) zwischen dem Zwischenglied (Z) und dem Abtriebsglied (A) ist die Bewegung des Zwischengliedes (Z) und damit die Bewegungsübertragung von der antreibenden Welle (W) auf das Abtriebsglied (A) und damit auf das Ventil (V) mit größerer Freiheit als beim Stand der Technik gestaltbar.Permits curve joint (za) between intermediate link (Z) and output link (A). With the cam joint (za) according to the invention between the intermediate member (Z) and the driven member (A), the movement of the intermediate member (Z) and thus the transmission of motion from the driving shaft (W) to the driven member (A) and thus to the valve ( V) can be designed with greater freedom than in the prior art.
Der zusätzliche Bewegungsfreiheitsgrad bewirkt ein Abrollen des Zwischengliedes (Z) am Abtriebsglied (A). Durch diese Drehbewegung wird eine Verdrängungsströmung des Schmiermittels bewirkt, die ihrerseits den Aufbau eines tragfähigen Schmierfilms im Kontakt von Zwischenglied (Z) und Abtriebsglied (A) maßgeblich unterstützt. Zusätzlich reduziert die Drehbewegung teilweise die Gleitgeschwindigkeit im Kontaktpunkt durch Abrollen. Jeder dieser Effekte vermindert die Reibung im erwähnten Kontaktpunkt.The additional degree of freedom of movement causes the intermediate link (Z) to roll off the output link (A). This rotary movement causes a displacement flow of the lubricant, which in turn significantly supports the build-up of a load-bearing lubricating film in the contact between the intermediate link (Z) and the output link (A). In addition, the rotary movement partially reduces the sliding speed at the contact point by rolling. Each of these effects reduces the friction at the contact point mentioned.
Die erfindungsgemäße Gestaltung besitzt zudem den Vorteil, keinen gegenüber dem Stand der Technik erhöhten Platzbedarf zu verursachen.The design according to the invention also has the advantage of not requiring more space than in the prior art.
In Patentanspruch 2 ist die vorteilhafte Gestaltung der Kontur (Kza oder Kaz) einer der beiden Kontaktpartner im Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) als ebene Fläche beschrieben. Hierdurch ist die Herstellung der Bauteile kostengünstiger und fertigungsgenauer als bei frei gestalteter Kontur beider Getriebeglieder.In claim 2, the advantageous design of the contour (Kza or Kaz) one of the two contact partners in the curved joint (za) between the intermediate member (Z) and output member (A) is described as a flat surface. As a result, the production of the components is more cost-effective and more precise than with a freely designed contour of both transmission elements.
In Patentanspruch 3 ist die vorteilhafte Gestaltung der Kontur (Kaz oder/und Kza) mindestens einer der beiden Kontaktpartner im Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) als Kreisbogen beschrieben. Hierdurch ist die Herstellung der Bauteile kostengünstiger und fertigungsgenauer als bei frei gestalteter Kontur der Getriebeglieder.In claim 3, the advantageous design of the contour (Kaz or / and Kza) of at least one of the two contact partners in the curved joint (za) between the intermediate member (Z) and the output member (A) is described as a circular arc. As a result, the production of the components is more cost-effective and more precise than with a freely designed contour of the gear members.
In den Patentansprüchen 4 - 7 sind weitere vorteilhafte Gestaltungen der Kurvengelenke beschrieben.Further advantageous designs of the curved joints are described in patent claims 4-7.
Durch eine Gestaltung eines Kurvengelenkes derart, daß die kurvengelenkbestimmende Kontur ausschließlich dem einen Kontaktpartner zugeordnet wird, wird die Kontur des anderen Kontaktpartners ein Kreisbogen oder ein Kreis, welcher vorteilhaft als umlauffähige Rolle ausgebildet ist. Hierdurch wird in diesem Kurvengelenk ein Abwälzen der Kontaktpartner an der die kurvengelenkbestimmenden Form erreicht und die Tangentialbewegung auf die Lagerung der umlauffähigen Rolle verschoben. Durch die bei Gleitlagern bekannten Werkstoffe und Schmierverhältnisse und durch Verwendung eines kleinen Reibradius wird so die Reibung in diesem Kurvengelenk vermindert.By designing a curve joint in such a way that the contour determining the curve joint is assigned exclusively to one contact partner, the contour of the other contact partner becomes an arc or a circle, which is advantageously designed as a rotatable roller. As a result, in this cam joint, the contact partners roll on the shape determining the cam joint and the tangential movement is shifted onto the bearing of the rotatable roller. Due to the materials and lubrication conditions known from plain bearings and the use of a small friction radius, the friction in this cam joint is reduced.
Patentanspruch 4 beschreibt eine Ausführung des Getriebes, bei welcher die kurvengelenkbestimmende Kontur des Kurvengelenkes (zg) zwischen Zwischenglied (Z) und Gehäuse (G) ausschließlich durch die Kontur (Kzgl) am Zwischenglied (Z) gebildet wird und die Kontur (Kgzl) der gehäuseseitigen Abstützung eine umlauffähige Rolle ist (Abbildung 2). Patentanspruch 5 beschreibt eine Ausführung des Getriebes, bei welcher die kurvengelenkbestimmende Kontur des Kurvengelenkes (zg) zwischen Zwischenglied (Z) und Gehäuse (G) ausschließlich durch die Kontur (Kgz2) am Gehäuse (G) gebildet wird und die zwischengliedseitige Kontur (Kzg2) eine umlauffähige Rolle ist (Abbildung 3).Claim 4 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zg) between the intermediate member (Z) and housing (G) is formed exclusively by the contour (Kzul) on the intermediate member (Z) and the contour (Kgzl) of the housing Support is a fit role (Figure 2). Claim 5 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zg) between the intermediate member (Z) and the housing (G) is formed exclusively by the contour (Kgz2) on the housing (G) and the intermediate-side contour (Kzg2) is one viable role is (Figure 3).
Patentanspruch 6 beschreibt eine Ausführung des Getriebes, bei welcher die kurvengelenkbestimmende Kontur des Kurvengelenkes (zw) zwischen Zwischenglied (Z) und Welle (W) ausschließlich durch die Kontur (Kwzl) an der Welle (W) gebildet wird und die zwischengliedseitige Kontur (Kzwl) eine umlauffähige Rolle ist (Abbildung 4).Claim 6 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (zw) between the intermediate member (Z) and the shaft (W) is formed exclusively by the contour (Kwzl) on the shaft (W) and the link-side contour (Kzwl) is a fit role (Figure 4).
Patentanspruch 7 beschreibt eine Ausführung des Getriebes, bei welcher die kurvengelenkbestimmende Kontur des Kurvengelenkes (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) ausschließlich durch die Kontur (Kazl) am Abtriebsglied (A) gebildet wird und die zwischengliedseitige Kontur (Kzal) ein Kreisbogen (Abbildung 5) oder eine umlauffähige Rolie,ist.Claim 7 describes an embodiment of the transmission, in which the curve-joint-determining contour of the curve joint (za) between the intermediate element (Z) and the output element (A) is formed exclusively by the contour (Kazl) on the output element (A) and the intermediate element-side contour (Kzal) Circular arc (Figure 5) or a fit Rolie.
In Patentanspruch 8 sind Ausführungsformen beschrieben, bei denen durch mehrfache Anwendung des reibungsmindernden Effekts in den Kurvengelenken am Zwischenglied (Z) die Reibung des Getriebes weiter abgesenkt wird.In claim 8 embodiments are described in which the friction of the transmission is further reduced by multiple use of the friction-reducing effect in the curved joints on the intermediate member (Z).
In Patentanspruch 9 sind Ausführungsformen der Kurvengelenke beschrieben, bei welchen jeweils durch Verwendung eines Wälzlagers zur Abstützung einer umlauffähigen Rolle die Reibung in den Kurvengelenken am Zwischenglied (Z) weiter vermindert wird.In claim 9, embodiments of the curved joints are described, in each of which by using a rolling bearing Supporting a wheel capable of movement, the friction in the curved joints on the intermediate link (Z) is further reduced.
Patentanspruch 10 beschreibt die vorteilhafte Gestaltung des Zwischengliedes (Z), bei welchem mindestens zwei der Kurvengelenke am Zwischenglied (Z) zwischengliedseitig durch Rotationskörper dargestellt werden und mindestens zwei der Drehmitten dieser Rotationskörper zusammenfallen. Auf diese Weise wird der Bauraum minimiert und die sic j&- aus der Drehbeschleunigung des Zwischengliedes (Z) ergebenden Kräfte werden verkleinert.Claim 10 describes the advantageous design of the intermediate member (Z), in which at least two of the curved joints on the intermediate member (Z) are represented on the intermediate member side by rotating bodies and at least two of the centers of rotation of these rotating bodies coincide. In this way, the installation space is minimized and the forces resulting from the rotational acceleration of the intermediate member (Z) are reduced.
Im Extremfall sind alle drei Kurvengelenke am Zwischenglied (Z) zwischengliedseitig durch Rotationskörper dargestellt und alle drei Drehmitten fallen zusammen (Abbildung 6). Auf diese Weise wird der kleinste Bauraumbedarf erzielt. Die Drehlage des Zwischengliedes (Z) als Bewegungsfreiheitsgrad ist dann für die Bewegungsübertragung ohne Bedeutung.In an extreme case, all three curved joints on the pontic (Z) are represented by rotating bodies on the pontic side and all three centers of rotation coincide (Figure 6). In this way, the smallest space requirement is achieved. The rotational position of the intermediate link (Z) as a degree of freedom of movement is then of no importance for the transmission of movement.
^^Patentanspruch 11 ist ausgeführt, daß durch eine gemeinsame Betätigung von mehreren Abtriebsgliedern (Ai) und Ventilen (Vi) eines Zylinders durch einen Nocken (N) und ein Zwischenglied (Z) die Gelenkzahl und die bewegten Massen vermindert werden können, was vorteilhaft die Reibung vermindert und über die Verkleinerung der Zahl der Bauteile zudem den Bauaufwand verkleinert (Abbildung 7).^^ Claim 11 is carried out that by a joint actuation of several output members (Ai) and valves (Vi) of a cylinder by a cam (N) and an intermediate member (Z), the number of joints and the moving masses can be reduced, which is advantageous Reduced friction and, by reducing the number of components, also reduced the construction effort (Figure 7).
In Patentansprüchen 12 und 13 ist ausgeführt, daß die das Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) bildende Kurve (Kgz2) im Gehäuse (G) aus einem die Ventilrast bildenden Teil (gl) und einem den Steuerbereich bildenden Teil (g2) besteht. Beispielsweise kann das den Steuerbereich bildende Teil (g2) in einem Schiebeteil (S) drehbar und das Schiebeteil (S) im Gehäuse (G) verschiebbar befestigt sein. Die Verschiebeposition (rs) des Schiebeteils (S) kann beispielsweise durch einen im Gehäuse (G) befestigten Nocken (VNs) eingestellt werden. DieIn claims 12 and 13 it is stated that the curve joint (zg) between the intermediate member (Z) and housing (G) forming curve (Kgz2) in the housing (G) from a part forming the valve latch (gl) and one Control area forming part (g2). For example, the part (g2) forming the control area can be rotatably mounted in a sliding part (S) and the sliding part (S) can be slidably mounted in the housing (G). The displacement position (rs) of the sliding part (S) can be set, for example, by a cam (VNs) fastened in the housing (G). The
Drehbewegung (rd) des den Steuerbereich bildenden Teils (g2) kann durch einen im Gehäuse (G) befestigten Nocken (VNd) oder durch einen im Schietbeteil (S) befestigten Nocken (VNd) eingestellt werden. Auf diese Weisest ist die Drehbewegung (rd) des den Steuerbereich bildenden Teils (g2) unabhängig von der Verschiebeposition (rs) des Schiebeteils (S) einstellbar. Im einfachsten Fall wird die Drehbewegung (rd) durch einen im Gehäuse (G) befindlichen Nocken durch die Verschiebung (rs) des Schiebeteils (S) gesteuert. Auf diese Weise kann zur Veränderung der Ventilhubkurve der Lage (a) der Steuerkurve in Rastrichtung verschiebbar (rv) und verdrehbar (rd) ausgeführt werden. Hierdurch wird die Gestaltungsfreiheit der Ventilhubkurve weiter erhöht. Ein Kontaktverlust der Getriebeglieder tritt nicht-auf. Insbesondere kann bei gleichem Ventilöffnungswinkel die Ventilbeschleunigung und der Ventilhub zusätzlich verändert werden (Abbildung 8).Rotational movement (rd) of the part (g2) forming the control area can be adjusted by a cam (VNd) fastened in the housing (G) or by a cam (VNd) fastened in the slant part (S). In this way, the rotary movement (rd) of the part (g2) forming the control area can be set independently of the displacement position (rs) of the sliding part (S). In the simplest case, the rotary movement (rd) is controlled by a cam in the housing (G) by the displacement (rs) of the sliding part (S). In this way, in order to change the valve lift curve, the position (a) of the control curve can be displaced (rv) and rotated (rd) in the latching direction. This further increases the design freedom of the valve lift curve. A loss of contact of the transmission members does not occur. In particular, with the same valve opening angle, the valve acceleration and valve lift can also be changed (Figure 8).
Das den Rastabschnitt bildende Teil (gl) im Gehäuse (G) kann dazu genutzt werden die Rückstellbewegung des Zwischengliedes (Z) und damit den Nockenkontakt zu gewährleisten, indem es im Gehäuse (G) drehbar gelagert ist und eine Kraft auf das Zwischenglied (Z) ausübt, welche dieses zum Nocken (N) hin bewegt. Diese Kraft wird beispielsweise über eine Federkraft (KF) erzeugt. Bei einer derartigen Gestaltung kann der erforderliche Federweg sehr klein ausgeführt sein (Abbildung 9). The part (gl) forming the latching section in the housing (G) can be used to ensure the return movement of the intermediate link (Z) and thus the cam contact by being rotatably mounted in the housing (G) and exerting a force on the intermediate link (Z) exercises which moves this towards the cam (N). This force is generated, for example, via a spring force (KF). With such a design, the required travel can be made very small (Figure 9).

Claims

Patentansprüche claims
1. Vorrichtung zur variablen Betätigung der Ladungswechselventile in Hubkolbenmotoren bestehend aus einem Gehäuse (G), einer im Gehäuse (G) drehbar gelagerten Welle (W), deren Bewegung von der1. Device for variable actuation of the charge exchange valves in reciprocating piston engines consisting of a housing (G), a shaft (W) rotatably mounted in the housing (G), the movement of which
Kurbelwelle abgeleitet ist, einem Abtriebsglied (A), welches im Gehäuse (G) eindeutig geführt ist und die Bewegung auf das Ladungswechselventil (V) überträgt und einem Zwischenglied (Z), welches mit der Welle (W) und mit dem Gehäuse (G) jeweils über genau ein Kurvengelenk (zw, zg) und mit dem Abtriebsglied (A) über ein weiteres Gelenk (za) verbunden ist, wobei die Kurve im Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) einen eine Rast bildenden Abschnitt und einen Steuerabschnitt aufweist, dessen Lage zur Welle (W) für die Veränderung der Ventilhubkurve einstellbar ist, dadurch gekennzeichnet, daß das Gelenk (za) zwischenCrankshaft is derived, an output member (A), which is clearly guided in the housing (G) and transmits the movement to the charge exchange valve (V) and an intermediate member (Z), which with the shaft (W) and with the housing (G) each via exactly one cam joint (zw, zg) and connected to the driven member (A) via a further joint (za), the curve in the cam joint (zg) between the intermediate member (Z) and the housing (G) forming a section forming a catch and has a control section, the position of which is adjustable relative to the shaft (W) for changing the valve lift curve, characterized in that the joint (za) between
Zwischenglied (Z) und Abtriebsglied (A) ein Kurvengelenk ist.Intermediate link (Z) and output link (A) is a cam joint.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß eine der das Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) bildenden Konturen (Kaz, Kza) am Zwischenglied (Z) und am2. Device according to claim 1, characterized in that one of the curve joint (za) between the intermediate member (Z) and the output member (A) forming contours (Kaz, Kza) on the intermediate member (Z) and on
Abtriebsglied (A) durch eine ebene Kontur gebildet wird.Output member (A) is formed by a flat contour.
3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß mindestens eine der das Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) bildenden Konturen (Kaz, Kza) am Zwischenglied (Z) und am Abtriebsglied (A) durch ein Segment eines umlauffähigen Rotationskörpers gebildet wird. 3. Apparatus according to claim 1, characterized in that at least one of the cam joint (za) between the intermediate member (Z) and the output member (A) forming contours (Kaz, Kza) on the intermediate member (Z) and on the output member (A) by a segment a rotatable body is formed.
. Vorrichtung nach den Ansprüchen 1-3, dadurch gekennzeichnet, daß das Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) durch einen im Gehäuse (G) angebrachten umlauffähigen Rotationskörper und durch eine Kurve (Kzgl) am Zwischenglied (Z) gebildet wird., Device according to claims 1-3, characterized in that the cam joint (zg) between the intermediate member (Z) and the housing (G) is formed by a rotatable body of rotation attached in the housing (G) and by a curve (Kzul) on the intermediate member (Z) becomes.
5. Vorrichtung nach den Ansprüchen 1-3, dadurch gekennzeichnet, daß das Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) durch einen am Zwischenglied (Z) angebrachten umlauffähigen5. Device according to claims 1-3, characterized in that the cam joint (zg) between the intermediate member (Z) and the housing (G) by a fit on the intermediate member (Z) fit for circulation
Rotationskörper und durch eine Kurve (Kgz2) im Gehäuse (G) gebildet wird.Rotational body and is formed by a curve (Kgz2) in the housing (G).
6. Vorrichtung nach den Ansprüchen 1-3, dadurch gekennzeichnet, daß das Kurvengelenk (zw) zwischen Zwischenglied (Z) und Welle (W) durch einen am Zwischenglied (Z) angebrachten umlauffähigen Rotationskörper und durch eine Kurve (Kwzl) an der Welle (W) gebildet wird.6. Device according to claims 1-3, characterized in that the cam joint (zw) between the intermediate member (Z) and shaft (W) by a rotatable body attached to the intermediate member (Z) and by a curve (Kwzl) on the shaft ( W) is formed.
7. Vorrichtung nach den Ansprüchen 1-3, dadurch gekennzeichnet, daß das Kurvengelenk (za) zwischen Zwischenglied (Z) und Abtriebsglied (A) durch einen am Zwischenglied (Z) angebrachten umlauffähigen Rotationskörper und durch eine Kurve (Kazl) am Abtriebsglied (A) gebildet wird. 7. Device according to claims 1-3, characterized in that the cam joint (za) between the intermediate member (Z) and output member (A) by a rotatable body attached to the intermediate member (Z) and by a curve (Kazl) on the output member (A ) is formed.
8. Vorrichtung nach den Ansprüchen 4-7, dadurch gekennzeichnet, daß wenigstens zwei der Kurvengelenke am Zwischenglied (Z) durch umlauffähige Rotationskörper gebildet werden.8. Device according to claims 4-7, characterized in that at least two of the cam joints on the intermediate member (Z) are formed by rotatable bodies.
9. Vorrichtung nach den Ansprüchen 4-8, dadurch gekennzeichnet, daß wenigstens einer der am Zwischenglied (Z) angebrachten umlauffähigen Rotationskörper durch einen Teil eines Wälzlagers gebildet wird.9. Device according to claims 4-8, characterized in that at least one of the rotatable body attached to the intermediate member (Z) is formed by part of a rolling bearing.
10. Vorrichtung nach den Ansprüchen 8 und 9, dadurch gekennzeichnet, daß wenigstens zwei der Drehmitten der am Zwischenglied (Z) angebrachten umlauffähigen Rotationskörper zusammenfallen.10. Device according to claims 8 and 9, characterized in that at least two of the centers of rotation of the rotatable body attached to the intermediate member (Z) coincide.
11. Vorrichtung nach den Ansprüchen 1-10, dadurch gekennzeichnet, daß von einem Zwischenglied (Z) über ein oder mehrere Abtriebsglieder (Ai) zwei oder mehrere Ventile (Vi) eines Zylinders betätigt werden.11. The device according to claims 1-10, characterized in that two or more valves (Vi) of a cylinder are actuated by an intermediate member (Z) via one or more output members (Ai).
12. Vorrichtung nach den Ansprüchen 8-11, dadurch gekennzeichnet, daß die das Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) bildende Kurve durch eine den Rastbereich bildende Kontur im Gehäuse oder an einem im Gehäuse befestigten Teil (gl) und durch eine den12. Device according to claims 8-11, characterized in that the curve joint (zg) between the intermediate member (Z) and housing (G) forming curve by a contour forming the latching area in the housing or on a part fastened in the housing (gl) and through a
Steuerbereich bildende Kontur an einem anderen Teil (g2) dargestellt wird.Control area forming contour is shown on another part (g2).
13. Vorrichtung nach Anspruch 6 dadurch gekennzeichnet, daß die das Kurvengelenk (zg) zwischen Zwischenglied (Z) und Gehäuse (G) bildende Steuerkurve bezüglich Verschiebung und Verdrehung veränderbar ist. 13. The apparatus according to claim 6, characterized in that the cam joint (zg) between the intermediate member (Z) and the housing (G) forming control curve is variable with respect to displacement and rotation.
EP02799032A 2001-12-20 2002-12-19 Device for variable actuation of the gas exchange valves in internal combustion piston engines Expired - Lifetime EP1458956B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10162797 2001-12-20
DE10162797A DE10162797A1 (en) 2001-12-20 2001-12-20 Device for variable actuation of the charge exchange valves in reciprocating engines
PCT/DE2002/004666 WO2003054362A1 (en) 2001-12-20 2002-12-19 Device for variable actuation of the gas exchange valves in internal combustion piston engines

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EP1458956A1 true EP1458956A1 (en) 2004-09-22
EP1458956B1 EP1458956B1 (en) 2008-05-07

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EP (1) EP1458956B1 (en)
AT (1) ATE394585T1 (en)
AU (1) AU2002364271A1 (en)
DE (2) DE10162797A1 (en)
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DE10162797A1 (en) 2001-12-20 2003-07-03 Schoen Helmut Device for variable actuation of the charge exchange valves in reciprocating engines
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ES2306810T3 (en) 2008-11-16
AU2002364271A1 (en) 2003-07-09
DE50212244D1 (en) 2008-06-19
DE10162797A1 (en) 2003-07-03
US20050028765A1 (en) 2005-02-10
WO2003054362A1 (en) 2003-07-03
ATE394585T1 (en) 2008-05-15
US7137368B2 (en) 2006-11-21
EP1458956B1 (en) 2008-05-07

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