EP2151548B1 - Valve drive for internal combustion engine, in particular with decompression-type braking system - Google Patents

Valve drive for internal combustion engine, in particular with decompression-type braking system Download PDF

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Publication number
EP2151548B1
EP2151548B1 EP09164653A EP09164653A EP2151548B1 EP 2151548 B1 EP2151548 B1 EP 2151548B1 EP 09164653 A EP09164653 A EP 09164653A EP 09164653 A EP09164653 A EP 09164653A EP 2151548 B1 EP2151548 B1 EP 2151548B1
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EP
European Patent Office
Prior art keywords
lever
valve
valve drive
rocker arm
gas exchange
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EP09164653A
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German (de)
French (fr)
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EP2151548A1 (en
Inventor
Oliver Schnell
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking

Definitions

  • the invention relates to a valve train for an internal combustion engine, in particular with a decompression brake.
  • the valve train comprises a camshaft with a cam, a tilting or rocking lever for transmitting the cam lift to a gas exchange valve, a tilting or rocker arm supporting swivel bearing and arranged in the power flow between the cam and the gas exchange valve hydraulic valve clearance compensation element.
  • valve engines for decompression brake internal combustion engines usually large volume diesel engines for the commercial vehicle sector - it is envisaged to reopen one or all exhaust valves of a cylinder during the compression stroke during the engine braking operation to significantly increase the charge cycle work in favor of negative engine performance.
  • the re-exhaust opening requires as a function of its timing significantly higher valve actuation forces, since the exhaust valves must open against the compression pressure and sometimes against the compression end pressure in the cylinder.
  • the lash adjuster As in the considered as generic US 7,392,772 B2 proposed in such valve trains, the compensation of the valve clearance by means of a hydraulic valve lash adjuster automatically and continuously, the lash adjuster is to be arranged as an alternative to a valve lash mechanically adjusting screw between the valve-side lever portion of a rocker arm disclosed there and the gas exchange valve.
  • this positioning of the lash adjuster may be problematic in that the high valve actuation forces during engine braking operation cause excessive lessening of the lash adjuster due to squeezing hydraulic fluid from its high pressure space.
  • the present invention is therefore based on the object to ensure the operability of a valve train of the type mentioned. Accordingly, it should also be possible in the case of very high valve actuation forces to equip the valve train with a hydraulic valve clearance compensation element of the known type for automatic and continuous adjustment of the valve clearance.
  • valve lash adjuster should be arranged stationarily in the internal combustion engine and the valve train further comprise a secondary lever with a first lever portion and a second lever portion.
  • the secondary lever is articulated between the lever sections on a tilting or rocker arm formed lever support, is supported by the first lever portion on the valve clearance compensation element and operated with the second lever portion of the gas exchange valve.
  • the effective lever arm of the first lever portion is significantly larger than the effective lever arm of the second lever portion.
  • the invention provides for a displacement of the valve lash adjuster in such a way that the valve lash adjuster no longer - as suggested in the cited prior art - moved with the gas exchange valve and the actuation forces is directly exposed, but a force-reducing lever ratio stationary in the Power flow between cam and gas exchange valve is integrated.
  • the effective lever arms have a transmission ratio of at least 2: 1.
  • the valve lash adjuster would be loaded at a valve actuation force of 15 kN and a gear ratio of 3: 1 only with a force of 5 kN.
  • the tilting or oscillating lever and the secondary lever should also be combined to form a captive unit.
  • the fulcrum may be a hinge pin attached to side walls of the rocker arm or rocker arm and spanning the side walls, forming a bolt joint with a hinge eye passing through the secondary lever transversely.
  • the pivot bearing should also be designed as an axis running parallel to the camshaft with a channel carrying a hydraulic medium and with a recess accommodating the valve lash adjuster and connected to the channel.
  • a particularly compact design of such a valve train is also given when the recess for the valve clearance compensation element in the axial region of the axis encompassing Lagerauges the tilting or rocking lever is arranged, wherein the bearing eye with a clearance for the valve clearance compensation element and / or the first lever portion of Secondary lever serving radial opening is provided.
  • the radial opening is preferably designed as a slot oriented in the circumferential direction of the bearing eye. This may be useful, for example, when the valve clearance compensation element protrudes through the radial opening and leads the tilting or rocking lever on the straight inner walls of the radial opening in the transverse direction to the axis.
  • the valve gear should further comprise a push rod, which is arranged in the transmission sense between the second lever portion of the secondary lever and the gas exchange valve.
  • a push rod for the purpose of assembly aid and operational Abspringêt for the push rod is a valve side End portion of the tilting or rocking lever be provided with a running in the direction of the gas exchange valve opening through which the push rod is passed.
  • both ends of the push rod should be designed as a joint head, wherein the lever-side condyle are received in a running on the second lever portion of the secondary lever socket and the valve-side condyle in a socket of the gas exchange valve frontally contacting pressure element.
  • FIG. 1 and 2 is a valve train 1 of an internal combustion engine with decompression brake in side view and in plan view disclosed.
  • One on one Swivel bearing 2 centrally supported rocker arm 3 is on the one hand with a cam 4 of a camshaft 5 in operative connection and on the other hand, a fulcrum 6, on which a secondary lever 7 is articulated between its first lever portion 8 and its second lever portion 9.
  • the secondary lever 7 is supported by the first lever portion 8 on a hydraulic valve clearance compensation element 10 and operated with the second lever portion 9 in the closing direction spring-loaded exhaust-side gas exchange valve, hereinafter referred to briefly as exhaust valve 11.
  • the rocker arm 3 and the secondary lever 7 are combined to form a captive assembly by the lever support 6 is formed as attached to projecting side walls 12 of the rocker arm 3 and the side walls 12 spanning hinge pin, with a secondary lever 7 transversely interspersing joint eye 13 (see FIG. 3 ) forms a pin joint.
  • the pivot bearing 2 is a basically known axis which is parallel to the camshaft 5 and is encompassed by a bearing eye 14 of the rocker arm 3 to form a sliding bearing.
  • the central axial region of the bearing eye 14 is provided with a radial opening 15, which is formed here as an oriented in the circumferential direction of the bearing eye 14 slot and depending on the extended position of the valve clearance compensation element 10 as a clearance for the valve clearance compensation element 10 and / or the first lever portion 8 of the secondary lever 7 is used.
  • the width of the slot 15 is also dimensioned so that the outer periphery of the valve lash adjuster 10 is only a slight axial play to keep the rocker arm 3 in the longitudinal direction of the axle 2 in position.
  • the known valve lash adjuster 10 is received in a recess 16 of the axis 2 and is supplied via a connected to the lubricant supply to the engine and the recess 16 intersecting channel 17 with hydraulic fluid.
  • valve-side end portion of the rocker arm 3 is provided with an opening extending in the direction of the outlet 11 opening 26, through which the push rod 20 with the required operating clearance passed through.
  • the effective lever arm of the first lever portion 8 is substantially larger than the effective lever arm of the second lever portion 9, wherein the effective lever arms in the illustrated embodiment have a transmission ratio of about 3: 1.
  • the distance between the lever support 6 and the contact point to the valve play compensation element 10 or to the push rod 20 is to be understood as meaning the effective lever arms. Due to the transmission ratio effective in the contact between the pressure piece 25 and the exhaust valve 11 valve actuating forces are reduced to 1/3 part of the supporting valve clearance compensation element 10 so that the caused by the squeezing of hydraulic fluid Absinkwert the valve lash adjuster 10 even at very high valve actuation forces a relatively low level can be maintained.
  • FIG. 4 A schematic overall view of the valve drive 1, which is only partially shown in the previous figures, starts FIG. 4 out.
  • the rocker arm 3 and the secondary lever 7 and the arrangement of the hydraulic valve lash adjuster 10 is the basic structure of the valve train 1 from the above cited US 7,392,772 B2 known and summarized here only briefly. Shown in plan view are the camshaft 5 with the cam 4, the axle 2, the rocker arm 3, the secondary lever 7, the lash adjuster 10, the fulcrum 6 and the exhaust valve 11.
  • the invention can be found not only in a rocker arm, but also in a rocker arm application.
  • the two lever types are known to differ by the position of the pivot bearing, wherein the rocker arm is not centrally but end-mounted and accordingly there run the cam and the gas exchange valve on the same lever portion.
  • valve drive according to the invention can also be used in cases in which very high valve actuation forces have to be controlled and yet a hydraulic valve clearance compensation is provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The valve train (1) has a camshaft (5) with a cam (4), where a valve clearance compensation element (10) is stationarily arranged in an internal combustion engine with a decompression brake. A secondary lever (7) is provided with two lever sections (8,9), where the secondary lever is hinged at a lever support (6).

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Ventiltrieb für eine Brennkraftmaschine insbesondere mit Dekompressionsbremse. Der Ventiltrieb umfasst eine Nockenwelle mit einem Nocken, einen Kipp- oder Schwinghebel zur Übertragung des Nockenhubs auf ein Gaswechselventil, ein den Kipp- oder Schwinghebel abstützendes Schwenklager und ein im Kraftfluss zwischen dem Nocken und dem Gaswechselventil angeordnetes hydraulisches Ventilspielausgleichselement.The invention relates to a valve train for an internal combustion engine, in particular with a decompression brake. The valve train comprises a camshaft with a cam, a tilting or rocking lever for transmitting the cam lift to a gas exchange valve, a tilting or rocker arm supporting swivel bearing and arranged in the power flow between the cam and the gas exchange valve hydraulic valve clearance compensation element.

Hintergrund der ErfindungBackground of the invention

Bei Ventiltrieben für Brennkraftmaschinen mit Dekompressionsbremse - üblicherweise großvolumige Dieselmotoren für den Nutzfahrzeugbereich - ist es vorgesehen, während des Motorbremsbetriebs ein oder alle Auslassventile eines Zylinders im Verlauf des Verdichtungstakts erneut zu öffnen, um die Ladungswechselarbeit zugunsten negativer Motorleistung deutlich zu erhöhen. Gegenüber der regulären Auslassventilbetätigung im Expansionstakt erfordert das erneute Auslassöffnen in Abhängigkeit von dessen Steuerzeiten deutlich höhere Ventilbetätigungskräfte, da die Auslassventile gegen den Verdichtungsdruck und mitunter gegen den Verdichtungsenddruck im Zylinder öffnen müssen.In valve engines for decompression brake internal combustion engines - usually large volume diesel engines for the commercial vehicle sector - it is envisaged to reopen one or all exhaust valves of a cylinder during the compression stroke during the engine braking operation to significantly increase the charge cycle work in favor of negative engine performance. Compared to the regular exhaust valve actuation in the expansion stroke, the re-exhaust opening requires as a function of its timing significantly higher valve actuation forces, since the exhaust valves must open against the compression pressure and sometimes against the compression end pressure in the cylinder.

Wie es in der als gattungsbildend betrachteten US 7,392,772 B2 vorgeschlagen ist, kann bei derartigen Ventiltrieben der Ausgleich des Ventilspiels auch mittels eines hydraulischen Ventilspielausgleichselements automatisch und stufenlos erfolgen, wobei das Ventilspielausgleichselement als Alternative zu einer das Ventilspiel mechanisch justierenden Einstellschraube zwischen dem ventilseitigen Hebelabschnitt eines dort offenbarten Kipphebels und dem Gaswechselventil angeordnet sein soll. Diese Positionierung des Ventilspielausgleichselements kann jedoch dahingehend problematisch sein, als die hohen Ventilbetätigungskräfte während des Motorbremsbetriebs ein übermäßiges Absinken des Ventilspielausgleichselements infolge Auspressens von Hydraulikmittel aus dessen Hochdruckraum bewirken. Die anschließend erforderliche Regeneration des Ventilspielausgleichselements wird zudem durch das Mehrfachöffnen des Auslassventils während einer Nockenumdrehung erschwert, da für das Nachsaugen von Hydraulikmittel in den dann expandierenden Hochdruckraum nur ein vergleichsweise kleiner hubfreier Nockenwinkel zur Verfügung steht. Eine Folge dieses Ungleichgewichts zwischen Absinken und Regeneration des Ventilspielausgleichselements kann, je nach Dauer des Motorbremsbetriebs, ein sukzessives vollständiges Zusammensinken des Ventilspielausgleichselements in seine mechanische Blockstellung sein, wobei dies mit einem sowohl in thermodynamischer Hinsicht als auch in mechanischer Hinsicht unzulässigen Abschneiden der Nockenerhebungen für den Expansionstakt und den Motorbremsbetrieb verbunden sein kann. Bezüglich der Thermodynamik seien der unzureichende Ladungswechsel aufgrund zu geringer Ventilöffnungsquerschnitte und bezüglich Mechanik die hohen Abhebe- und Aufsetzgeschwindigkeiten des Gaswechselventils infolge fehlender Nockenrampen zu nennen.As in the considered as generic US 7,392,772 B2 proposed in such valve trains, the compensation of the valve clearance by means of a hydraulic valve lash adjuster automatically and continuously, the lash adjuster is to be arranged as an alternative to a valve lash mechanically adjusting screw between the valve-side lever portion of a rocker arm disclosed there and the gas exchange valve. However, this positioning of the lash adjuster may be problematic in that the high valve actuation forces during engine braking operation cause excessive lessening of the lash adjuster due to squeezing hydraulic fluid from its high pressure space. The subsequently required regeneration of the valve lash adjuster is also made more difficult by the multiple opening of the exhaust valve during a cam revolution, since only a comparatively small lift-free cam angle is available for the suction of hydraulic fluid in the then expanding high-pressure chamber. A consequence of this disequilibrium between dropping and regenerating the lash adjuster may, depending on the duration of the engine braking operation, be a successive complete collapse of the lash adjuster into its mechanical block position, with both thermodynamic and mechanical disallowance of the cam lobes for the expansion stroke and the engine braking operation may be connected. With regard to thermodynamics, the insufficient charge exchange due to insufficient valve opening cross-sections and with regard to mechanics, the high lifting and Aufsetzgeschwindigkeiten the gas exchange valve due to lack of cam ramps are mentioned.

Diese Betrachtungen gelten in entsprechender Weise für den in der DE 10 2006 031 706 A1 vorgeschlagenen Ventiltrieb mit einem hydraulischen Ventilspielausgleichselement, das zwischen einem Kipphebel und dem Gaswechselventil angeordnet ist.These considerations apply in a similar way to those in the DE 10 2006 031 706 A1 proposed valve train with a hydraulic valve clearance compensation element, which is arranged between a rocker arm and the gas exchange valve.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, die Funktionsfähigkeit eines Ventiltriebs der eingangs genannten Art sicherzustellen. Demnach soll es auch im Falle sehr hoher Ventilbetätigungskräfte möglich sein, den Ventiltrieb mit einem hydraulischen Ventilspielausgleichselement der an sich bekannten Art zur automatischen und stufenlosen Einstellung des Ventilspiels auszustatten.The present invention is therefore based on the object to ensure the operability of a valve train of the type mentioned. Accordingly, it should also be possible in the case of very high valve actuation forces to equip the valve train with a hydraulic valve clearance compensation element of the known type for automatic and continuous adjustment of the valve clearance.

Zusammenfassung der ErfindungSummary of the invention

Die Lösung dieser Aufgabe ergibt sich aus den kennzeichnenden Merkmalen des Anspruchs 1, während vorteilhafte Weiterbildungen und Ausgestaltungen der Erfindung den Unteransprüchen entnehmbar sind. Demnach sollen das Ventilspielausgleichselement stationär in der Brennkraftmaschine angeordnet sein und der Ventiltrieb weiterhin einen Sekundärhebel mit einem ersten Hebelabschnitt und einem zweiten Hebelabschnitt umfassen. Dabei ist der Sekundärhebel zwischen den Hebelabschnitten an einer am Kipp- oder Schwinghebel ausgebildeten Hebelstütze angelenkt, stützt sich mit dem ersten Hebelabschnitt auf dem Ventilspielausgleichselement ab und betätigt mit dem zweiten Hebelabschnitt das Gaswechselventil. Der wirksame Hebelarm des ersten Hebelabschnitts ist deutlich größer als der wirksame Hebelarm des zweiten Hebelabschnitts.The solution of this problem arises from the characterizing features of claim 1, while advantageous developments and refinements of the invention are the dependent claims can be removed. Accordingly, the valve lash adjuster should be arranged stationarily in the internal combustion engine and the valve train further comprise a secondary lever with a first lever portion and a second lever portion. In this case, the secondary lever is articulated between the lever sections on a tilting or rocker arm formed lever support, is supported by the first lever portion on the valve clearance compensation element and operated with the second lever portion of the gas exchange valve. The effective lever arm of the first lever portion is significantly larger than the effective lever arm of the second lever portion.

Mit anderen Worten sieht die Erfindung eine Verlagerung des Ventilspielausgleichselements in der Weise vor, dass das Ventilspielausgleichselement nicht mehr - wie im eingangs zitierten Stand der Technik vorgeschlagen - mit dem Gaswechselventil mitbewegt und dessen Betätigungskräften unmittelbar ausgesetzt ist, sondern über ein Kräfte reduzierendes Hebelverhältnis stationär in den Kraftfluss zwischen Nocken und Gaswechselventil eingebunden ist.In other words, the invention provides for a displacement of the valve lash adjuster in such a way that the valve lash adjuster no longer - as suggested in the cited prior art - moved with the gas exchange valve and the actuation forces is directly exposed, but a force-reducing lever ratio stationary in the Power flow between cam and gas exchange valve is integrated.

In einer bezüglich des Hebelverhältnisses bevorzugten Konkretisierung der Erfindung ist es vorgesehen, dass die wirksamen Hebelarme ein Übersetzungsverhältnis von mindestens 2:1 aufweisen. Beispielsweise würde demnach das Ventilspielausgleichselement bei einer Ventilbetätigungskraft von 15 kN und einem Übersetzungsverhältnis von 3:1 lediglich mit einer Kraft von 5 kN belastet werden.In a preferred relative to the lever ratio concretization of the invention, it is provided that the effective lever arms have a transmission ratio of at least 2: 1. For example, therefore, the valve lash adjuster would be loaded at a valve actuation force of 15 kN and a gear ratio of 3: 1 only with a force of 5 kN.

Zur Reduzierung des Montageaufwandes sollen ferner der Kipp- oder Schwinghebel und der Sekundärhebel zu einer verliersicheren Baueinheit zusammengefasst sein. Dabei kann es sich bei der Hebelstütze um einen an Seitenwänden des Kipp- oder Schwinghebels befestigten und die Seitenwände überspannenden Gelenkbolzen handeln, der mit einem den Sekundärhebel quer durchsetzenden Gelenkauge ein Bolzengelenk bildet.To reduce the assembly costs, the tilting or oscillating lever and the secondary lever should also be combined to form a captive unit. In this case, the fulcrum may be a hinge pin attached to side walls of the rocker arm or rocker arm and spanning the side walls, forming a bolt joint with a hinge eye passing through the secondary lever transversely.

Entsprechend einem später erläuterten Ausführungsbeispiel der Erfindung soll außerdem das Schwenklager als parallel zur Nockenwelle verlaufende Achse mit einem Hydraulikmittel führenden Kanal und mit einer das Ventilspielausgleichselement aufnehmenden und an den Kanal angeschlossenen Ausnehmung ausgebildet sein. Eine besonders kompakte Ausgestaltung eines solchen Ventiltriebs ist ferner dann gegeben, wenn die Ausnehmung für das Ventilspielausgleichselement im Axialbereich eines die Achse umgreifenden Lagerauges des Kipp- oder Schwinghebels angeordnet ist, wobei das Lagerauge mit einer als Freigang für das Ventilspielausgleichselement und/oder den ersten Hebelabschnitt des Sekundärhebels dienenden Radialöffnung versehen ist. Vorzugsweise ist die Radialöffnung als in Umfangsrichtung des Lagerauges orientiertes Langloch ausgebildet. Dies kann beispielsweise dann zweckmäßig sein, wenn das Ventilspielausgleichselement durch die Radialöffnung hindurch ragt und den Kipp- oder Schwinghebel an den geraden Innenwänden der Radialöffnung in Querrichtung zur Achse führt.According to an embodiment of the invention explained later, the pivot bearing should also be designed as an axis running parallel to the camshaft with a channel carrying a hydraulic medium and with a recess accommodating the valve lash adjuster and connected to the channel. A particularly compact design of such a valve train is also given when the recess for the valve clearance compensation element in the axial region of the axis encompassing Lagerauges the tilting or rocking lever is arranged, wherein the bearing eye with a clearance for the valve clearance compensation element and / or the first lever portion of Secondary lever serving radial opening is provided. The radial opening is preferably designed as a slot oriented in the circumferential direction of the bearing eye. This may be useful, for example, when the valve clearance compensation element protrudes through the radial opening and leads the tilting or rocking lever on the straight inner walls of the radial opening in the transverse direction to the axis.

In weiterer Ausgestaltung der Erfindung soll der Ventiltrieb weiterhin eine Stößelstange umfassen, die im Übertragungssinn zwischen dem zweiten Hebelabschnitt des Sekundärhebels und dem Gaswechselventil angeordnet ist. Zwecks Montagehilfe und betrieblicher Abspringsicherung für die Stößelstange soll ein ventilseitiger Endabschnitt des Kipp- oder Schwinghebels mit einer in Richtung des Gaswechselventils verlaufenden Öffnung versehen sein, durch welche die Stößelstange hindurchgeführt ist. Zudem sollen beide Enden der Stößelstange als Gelenkkopf ausgebildet sein, wobei der hebelseitige Gelenkkopf in einer am zweiten Hebelabschnitt des Sekundärhebels verlaufenden Gelenkpfanne und der ventilseitige Gelenkkopf in einer Gelenkpfanne eines das Gaswechselventil stirnseitig kontaktierenden Druckstücks aufgenommen sind.In a further embodiment of the invention, the valve gear should further comprise a push rod, which is arranged in the transmission sense between the second lever portion of the secondary lever and the gas exchange valve. For the purpose of assembly aid and operational Abspringsicherung for the push rod is a valve side End portion of the tilting or rocking lever be provided with a running in the direction of the gas exchange valve opening through which the push rod is passed. In addition, both ends of the push rod should be designed as a joint head, wherein the lever-side condyle are received in a running on the second lever portion of the secondary lever socket and the valve-side condyle in a socket of the gas exchange valve frontally contacting pressure element.

Schließlich sollen, sofern es möglich und zweckmäßig ist, die vorgenannten Merkmale auch beliebig miteinander kombinierbar sein.Finally, as far as possible and expedient, the abovementioned features should also be combinable with one another as desired.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen, in denen ein Ausführungsbeispiel mit den für das Verständnis der Erfindung wesentlichen Bauteilen und Merkmalen dargestellt ist. Es zeigen:

Figur 1
einen Ausschnitt eines Kipphebel-Ventiltriebs in Seitenansicht;
Figur 2
den Ventiltrieb gemäß Figur 1 in Draufsicht;
Figur 3
den Schnitt I-I gemäß Figur 2;
Figur 4
den Kipphebel-Ventiltrieb gemäß Figur 1 in schematischer Gesamtdar- stellung und
Figur 5
den Schnitt II-II gemäß Figur 4.
Further features of the invention will become apparent from the following description and from the drawings, in which an embodiment is shown with the essential for understanding the invention components and features. Show it:
FIG. 1
a detail of a rocker valve drive in side view;
FIG. 2
according to the valve train FIG. 1 in plan view;
FIG. 3
the section II according to FIG. 2 ;
FIG. 4
the toggle valve gear according to FIG. 1 in schematic overall representation and
FIG. 5
Section II-II according to FIG. 4 ,

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

In den Figuren 1 und 2 ist ein Ventiltrieb 1 einer Brennkraftmaschine mit Dekompressionsbremse in Seitenansicht bzw. in Draufsicht offenbart. Ein auf einem Schwenklager 2 zentral abgestützter Kipphebel 3 steht einerseits mit einem Nocken 4 einer Nockenwelle 5 in Wirkverbindung und weist andererseits eine Hebelstütze 6 auf, an der ein Sekundärhebel 7 zwischen seinem ersten Hebelabschnitt 8 und seinem zweiten Hebelabschnitt 9 angelenkt ist. Der Sekundärhebel 7 stützt sich mit dem ersten Hebelabschnitt 8 auf einem hydraulischen Ventilspielausgleichselement 10 ab und betätigt mit dem zweiten Hebelabschnitt 9 ein in Schließrichtung federkraftbeaufschlagtes auslassseitiges Gaswechselventil, nachfolgend kurz als Auslassventil 11 bezeichnet.In the Figures 1 and 2 is a valve train 1 of an internal combustion engine with decompression brake in side view and in plan view disclosed. One on one Swivel bearing 2 centrally supported rocker arm 3 is on the one hand with a cam 4 of a camshaft 5 in operative connection and on the other hand, a fulcrum 6, on which a secondary lever 7 is articulated between its first lever portion 8 and its second lever portion 9. The secondary lever 7 is supported by the first lever portion 8 on a hydraulic valve clearance compensation element 10 and operated with the second lever portion 9 in the closing direction spring-loaded exhaust-side gas exchange valve, hereinafter referred to briefly as exhaust valve 11.

Der Kipphebel 3 und der Sekundärhebel 7 sind zu einer verliersicheren Baueinheit zusammengefasst, indem die Hebelstütze 6 als an vorspringenden Seitenwänden 12 des Kipphebels 3 befestigter und die Seitenwände 12 überspannender Gelenkbolzen ausgebildet ist, der mit einem den Sekundärhebel 7 quer durchsetzenden Gelenkauge 13 (siehe Figur 3) ein Bolzengelenk bildet.The rocker arm 3 and the secondary lever 7 are combined to form a captive assembly by the lever support 6 is formed as attached to projecting side walls 12 of the rocker arm 3 and the side walls 12 spanning hinge pin, with a secondary lever 7 transversely interspersing joint eye 13 (see FIG. 3 ) forms a pin joint.

Bei dem Schwenklager 2 handelt es sich um eine grundsätzlich bekannte Achse, die parallel zur Nockenwelle 5 verläuft und von einem Lagerauge 14 des Kipphebels 3 unter Bildung eines Gleitlagers umgriffen wird. Der mittlere Axialbereich des Lagerauges 14 ist mit einer Radialöffnung 15 versehen, die hier als in Umfangsrichtung des Lagerauges 14 orientiertes Langloch ausgebildet ist und je nach Ausfahrstellung des Ventilspielausgleichselements 10 als Freigang für das Ventilspielausgleichselement 10 und/oder den ersten Hebelabschnitt 8 des Sekundärhebels 7 dient. Die Breite des Langlochs 15 ist zudem so bemessen, dass zum Außenumfang des Ventilspielausgleichselements 10 ein lediglich geringes Axialspiel besteht, um den Kipphebel 3 in Längsrichtung der Achse 2 in Position zu halten.In the pivot bearing 2 is a basically known axis which is parallel to the camshaft 5 and is encompassed by a bearing eye 14 of the rocker arm 3 to form a sliding bearing. The central axial region of the bearing eye 14 is provided with a radial opening 15, which is formed here as an oriented in the circumferential direction of the bearing eye 14 slot and depending on the extended position of the valve clearance compensation element 10 as a clearance for the valve clearance compensation element 10 and / or the first lever portion 8 of the secondary lever 7 is used. The width of the slot 15 is also dimensioned so that the outer periphery of the valve lash adjuster 10 is only a slight axial play to keep the rocker arm 3 in the longitudinal direction of the axle 2 in position.

Wie es aus dem in Figur 3 gezeigten Schnitt I-I deutlich wird, ist das an sich bekannte Ventilspielausgleichselement 10 in einer Ausnehmung 16 der Achse 2 aufgenommen und wird über einen an die Schmiermittelversorgung der Brennkraftmaschine angeschlossenen und die Ausnehmung 16 schneidenden Kanal 17 mit Hydraulikmittel versorgt. Zur Druckentlastung dient eine den Grund der Ausnehmung 16 schneidende Achsbohrung 18, die zumindest in der gezeigten hubfreien Stellung des Kipphebels 3 über eine Kipphebelbohrung 19 mit der Umgebung des Kipphebels 3 kommuniziert.As it is from the in FIG. 3 shown section II is clear, the known valve lash adjuster 10 is received in a recess 16 of the axis 2 and is supplied via a connected to the lubricant supply to the engine and the recess 16 intersecting channel 17 with hydraulic fluid. To depressurize a serving the bottom of the recess 16 intersecting axial bore 18, at least in the stroke-free shown Position of the rocker arm 3 via a Kipphebelbohrung 19 communicates with the environment of the rocker arm 3.

Die Betätigung des Auslassventils 11 erfolgt mittels einer Stößelstange 20, die zwischen dem zweiten Hebelabschnitt 9 des Sekundärhebels 7 und dem Auslassventil 11 angeordnet ist und deren beide Enden 21, 22 als sphärischer Gelenkkopf ausgebildet sind. Dabei sind der hebelseitige Gelenkkopf 21 in einer im zweiten Hebelabschnitt 9 verlaufenden Gelenkpfanne 23 und der ventilseitige Gelenkkopf 22 in einer Gelenkpfanne 24 eines das Auslassventil 11 stirnseitig kontaktierenden Druckstücks 25 aufgenommen. Die Gelenkpfannen 23, 24 sind kalottenförmig ausgebildet.The actuation of the outlet valve 11 by means of a push rod 20 which is arranged between the second lever portion 9 of the secondary lever 7 and the outlet valve 11 and whose two ends 21, 22 are formed as a spherical joint head. Here, the lever-side condyle 21 in a second lever portion 9 extending in the socket 23 and the valve-side condyle 22 in a joint socket 24 of the outlet valve 11 frontally contacting pressure piece 25 are added. The sockets 23, 24 are formed dome-shaped.

Zur vereinfachten Montage des Ventiltriebs 1 und um ein ungewolltes Abspringen der Stößelstange 20 während des Betriebs der Brennkraftmaschine zu verhindern, ist der ventilseitige Endabschnitt des Kipphebels 3 mit einer in Richtung des Auslassventils 11 verlaufenden Öffnung 26 versehen, durch welche die Stößelstange 20 mit dem erforderlichen Betriebsspiel hindurchgeführt ist.For simplified assembly of the valve gear 1 and to prevent accidental jumping off of the push rod 20 during operation of the internal combustion engine, the valve-side end portion of the rocker arm 3 is provided with an opening extending in the direction of the outlet 11 opening 26, through which the push rod 20 with the required operating clearance passed through.

Bei Betrachtung des Sekundärhebels 7 in Figur 3 wird ferner deutlich, dass der wirksame Hebelarm des ersten Hebelabschnitts 8 wesentlich größer als der wirksame Hebelarm des zweiten Hebelabschnitts 9 ist, wobei die wirksamen Hebelarme im gezeigten Ausführungsbeispiel ein Übersetzungsverhältnis von etwa 3:1 aufweisen. Unter den wirksamen Hebelarmen ist jeweils der Abstand zwischen der Hebelstütze 6 und dem Kontaktpunkt zum Ventilspielausgleichselement 10 bzw. zur Stößelstange 20 zu verstehen. Aufgrund des Übersetzungsverhältnisses werden die im Kontakt zwischen dem Druckstück 25 und dem Auslassventil 11 wirksamen Ventilbetätigungskräfte in guter Näherung auf 1/3 seitens des abstützenden Ventilspielausgleichselements 10 reduziert, so dass der durch das Auspressen von Hydraulikmittel bedingte Absinkwert des Ventilspielausgleichselements 10 auch bei sehr hohen Ventilbetätigungskräften auf einem vergleichsweise geringen Niveau gehalten werden kann.Looking at the secondary lever 7 in FIG. 3 It is also clear that the effective lever arm of the first lever portion 8 is substantially larger than the effective lever arm of the second lever portion 9, wherein the effective lever arms in the illustrated embodiment have a transmission ratio of about 3: 1. In each case the distance between the lever support 6 and the contact point to the valve play compensation element 10 or to the push rod 20 is to be understood as meaning the effective lever arms. Due to the transmission ratio effective in the contact between the pressure piece 25 and the exhaust valve 11 valve actuating forces are reduced to 1/3 part of the supporting valve clearance compensation element 10 so that the caused by the squeezing of hydraulic fluid Absinkwert the valve lash adjuster 10 even at very high valve actuation forces a relatively low level can be maintained.

Eine schematische Gesamtdarstellung des in den vorherigen Figuren nur teilweise dargestellten Ventiltriebs 1 geht aus Figur 4 hervor. Abgesehen von der erfindungsgemäßen Ausgestaltung des Kipphebels 3 und des Sekundärhebels 7 sowie der Anordnung des hydraulischen Ventilspielausgleichselements 10 ist der grundsätzliche Aufbau des Ventiltriebs 1 aus der eingangs zitierten US 7,392,772 B2 bekannt und an dieser Stelle nur kurz zusammengefasst. In Draufsicht dargestellt sind die Nockenwelle 5 mit dem Nocken 4, die Achse 2, der Kipphebel 3, der Sekundärhebel 7, das Ventilspielausgleichselement 10, die Hebelstütze 6 und das Auslassventil 11.A schematic overall view of the valve drive 1, which is only partially shown in the previous figures, starts FIG. 4 out. Apart from the inventive design of the rocker arm 3 and the secondary lever 7 and the arrangement of the hydraulic valve lash adjuster 10 is the basic structure of the valve train 1 from the above cited US 7,392,772 B2 known and summarized here only briefly. Shown in plan view are the camshaft 5 with the cam 4, the axle 2, the rocker arm 3, the secondary lever 7, the lash adjuster 10, the fulcrum 6 and the exhaust valve 11.

Das eingangs erwähnte erneute Öffnen des Auslassventils 11 während des Verdichtungstakts wird durch einen separaten Bremsnocken 27 erzeugt, der mit einem als Bremshebel 28 bezeichneten weiteren Kipphebel in Wirkverbindung steht. Wie es in Zusammenschau mit dem in Figur 5 dargestellten Schnitt II-II deutlich wird, ist der Kipphebel 3 mit einem seitlichen Fortsatz 29 versehen, der den Bremshebel 28 mit einem hydraulisch betätigten Koppelkolben 30 untergreift. Lediglich während des Motorbremsbetriebs befindet sich der Koppelkolben 30 in der dargestellten ausgefahrenen Position, so dass die Schwenkbewegung des Bremshebels 28 über den Koppelkolben 30, den Kipphebel 3 und den Sekundärhebel 7 auf das Auslassventil 11 übertragen wird.The above-mentioned reopening of the exhaust valve 11 during the compression stroke is generated by a separate brake cam 27, which is in operative connection with a designated as a brake lever 28 further rocker arm. As it is in synopsis with the in FIG. 5 shown section II-II becomes clear, the rocker arm 3 is provided with a lateral extension 29 which engages under the brake lever 28 with a hydraulically actuated coupling piston 30. Only during the engine braking operation, the coupling piston 30 is in the illustrated extended position, so that the pivotal movement of the brake lever 28 via the coupling piston 30, the rocker arm 3 and the secondary lever 7 is transmitted to the exhaust valve 11.

Ferner sei noch darauf hingewiesen, dass die Erfindung nicht nur bei einem Kipphebel, sondern auch bei einem Schwinghebel Anwendung finden kann. Die beiden Hebelarten unterscheiden sich bekanntermaßen durch die Position des Schwenklagers, wobei der Schwinghebel nicht zentral, sondern endseitig gelagert ist und dementsprechend dort der Nocken und das Gaswechselventil an demselben Hebelabschnitt verlaufen.It should also be noted that the invention can be found not only in a rocker arm, but also in a rocker arm application. The two lever types are known to differ by the position of the pivot bearing, wherein the rocker arm is not centrally but end-mounted and accordingly there run the cam and the gas exchange valve on the same lever portion.

Schließlich sei auch darauf hingewiesen, dass die Erfindung zwar bevorzugt, jedoch nicht ausschließlich in Zusammenhang mit einer Dekompressionsbremse vorgesehen ist. Ein erfindungsgemäßer Ventiltrieb kann vielmehr auch in solchen Fällen Anwendung finden, in denen sehr hohe Ventilbetätigungskräfte zu beherrschen sind und dennoch ein hydraulischer Ventilspielausgleich vorgesehen ist.Finally, it should also be noted that although the invention is preferably, but not exclusively provided in connection with a decompression brake. On the contrary, a valve drive according to the invention can also be used in cases in which very high valve actuation forces have to be controlled and yet a hydraulic valve clearance compensation is provided.

Bezugszahlenreference numerals

11
Ventiltriebvalve train
22
Schwenklager / AchseSwivel bearing / axle
33
Kipphebelrocker arm
44
Nockencam
55
Nockenwellecamshaft
66
Hebelstützefulcrum
77
Sekundärhebelsecondary lever
88th
erster Hebelabschnitt des Sekundärhebelsfirst lever portion of the secondary lever
99
zweiter Hebelabschnitt des Sekundärhebelssecond lever portion of the secondary lever
1010
VentilspielausgleichselementLash adjuster
1111
Auslassventil / GaswechselventilExhaust valve / gas exchange valve
1212
Seitenwand des KipphebelsSidewall of the rocker arm
1313
Gelenkaugejoint eye
1414
Lageraugebearing eye
1515
Radialöffnungradial opening
1616
Ausnehmungrecess
1717
Kanalchannel
1818
Achsbohrungaxle bore
1919
KipphebelbohrungKipphebelbohrung
2020
Stößelstangepushrod
2121
Ende der Stößelstange / hebelseitiger GelenkkopfEnd of the push rod / lever-side condyle
2222
Ende der Stößelstange / ventilseitiger GelenkkopfEnd of the pushrod / valve-side condyle
2323
Gelenkpfanne des SekundärhebelsJoint socket of the secondary lever
2424
Gelenkpfanne des DruckstücksSocket of the pressure piece
2525
DruckstückPressure piece
2626
Öffnung des KipphebelsOpening of the rocker arm
2727
Bremsnockenbrake cams
2828
Bremshebelbrake lever
2929
seitlicher Fortsatzlateral extension
3030
Koppelkolbencoupling pistons

Claims (10)

  1. Valve drive (1) for an internal combustion engine, in particular with a decompression brake, comprising a camshaft (5) with a cam (4), comprising a rocker arm (3) or oscillating lever for transmitting the cam stroke to a gas exchange valve (11), comprising a pivot bearing (2) which supports the rocker arm (3) or oscillating lever, and comprising a hydraulic valve play compensating element (10) which is arranged in the force flow between the cam (4) and the gas exchange valve (11), characterized in that the valve play compensating element (10) is arranged in a stationary fashion in the internal combustion engine and the valve drive (1) also comprises a secondary lever (7) having a first lever section (8) and having a second lever section (9), which secondary lever (7) is articulatedly connected, between the lever sections (8, 9), to a lever support (6) formed on the rocker arm (3) or oscillating lever, is supported with the first lever section (8) on the valve play compensating element (10) and actuates the gas exchange valve (11) by means of the second lever section (9), with the effective lever arm of the first lever section (8) being considerably greater than the effective lever arm of the second lever section (9).
  2. Valve drive (1) according to Claim 1, characterized in that the effective lever arms have a transmission ratio of at least 2:1.
  3. Valve drive (1) according to Claim 1, characterized in that the rocker arm (3) or oscillating lever and the secondary lever (7) are combined to form a captive structural unit.
  4. Valve drive (1) according to Claim 3, characterized in that the lever support (6) is a joint pin which is fastened to side walls (12) of the rocker arm (3) or oscillating lever and which spans the side walls (12) and which, together with a joint eyelet (13) which extends transversely through the secondary lever (7), forms a pin joint.
  5. Valve drive (1) according to Claim 1, characterized in that the pivot bearing (2) is formed as an axle which runs parallel to the camshaft (5) and which has a hydraulic-medium-conducting duct (17) and a recess (16) which holds the valve play compensating element (10) and which is connected to the duct (17).
  6. Valve drive (1) according to Claim 5, characterized in that the recess (16) for the valve play compensating element (10) is arranged in the axial region of a bearing eyelet (14), which engages around the axle (2), of the rocker arm (3) or oscillating lever, with the bearing eyelet (14) being provided with a radial opening (15) which serves as a clearance for the valve play compensating element (10) and/or for the first lever section (8) of the secondary lever (7).
  7. Valve drive (1) according to Claim 6, characterized in that the radial opening (15) is formed as a slot which is aligned in the circumferential direction of the bearing eyelet (14).
  8. Valve drive (1) according to Claim 1, characterized in that the valve drive (1) also comprises a tappet rod (20) which is arranged, for the purpose of transmission, between the second lever section (9) of the secondary lever (7) and the gas exchange valve (11).
  9. Valve drive (1) according to Claim 8, characterized in that a valve-side end section of the rocker arm (3) or oscillating lever is provided with an opening (26) which runs in the direction of the gas exchange valve (11) and through which opening (26) the tappet rod (20) is guided.
  10. Valve drive (1) according to Claim 8, characterized in that both ends (21, 22) of the tappet rod (20) are designed as joint heads, with the lever-side joint head (21) being held in a joint socket (23) which runs on the second lever section (9) of the secondary lever (7) and with the valve-side joint head (22) being held in a joint socket (24) of a thrust piece (25) which makes contact at the end side with the gas exchange valve (11).
EP09164653A 2008-08-08 2009-07-06 Valve drive for internal combustion engine, in particular with decompression-type braking system Active EP2151548B1 (en)

Applications Claiming Priority (1)

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DE102008037158A DE102008037158A1 (en) 2008-08-08 2008-08-08 Valve drive for an internal combustion engine, in particular with decompression brake

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EP2151548A1 EP2151548A1 (en) 2010-02-10
EP2151548B1 true EP2151548B1 (en) 2011-05-18

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US (1) US8042502B2 (en)
EP (1) EP2151548B1 (en)
AT (1) ATE510110T1 (en)
DE (1) DE102008037158A1 (en)

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US9512786B2 (en) * 2012-09-25 2016-12-06 Renault Trucks Valve actuation mechanism and automotive vehicle equipped with such a valve actuation mechanism
CN106536879A (en) * 2014-04-03 2017-03-22 博格华纳公司 Locking cylinder pressure relief actuator
KR101980814B1 (en) * 2014-06-10 2019-05-21 자콥스 비히클 시스템즈, 인코포레이티드. Linkage between an auxiliary motion source and a main motion load path in an internal combustion engine
ES2661164T3 (en) * 2015-02-24 2018-03-27 Fpt Industrial S.P.A. Valve drive system of an internal combustion engine
EP3061926B1 (en) * 2015-02-24 2018-12-26 FPT Industrial S.p.A. Valve actuation system of an internal combustion engine
CN114542230B (en) * 2022-02-23 2022-11-29 湖南道依茨动力有限公司 In-cylinder braking and valve clearance adjusting method, adjusting structure and engine

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Also Published As

Publication number Publication date
EP2151548A1 (en) 2010-02-10
ATE510110T1 (en) 2011-06-15
US8042502B2 (en) 2011-10-25
DE102008037158A1 (en) 2010-02-11
US20100031907A1 (en) 2010-02-11

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