EP2090757B1 - Tilt lever assembly with a bearing with slots - Google Patents

Tilt lever assembly with a bearing with slots Download PDF

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Publication number
EP2090757B1
EP2090757B1 EP08018202A EP08018202A EP2090757B1 EP 2090757 B1 EP2090757 B1 EP 2090757B1 EP 08018202 A EP08018202 A EP 08018202A EP 08018202 A EP08018202 A EP 08018202A EP 2090757 B1 EP2090757 B1 EP 2090757B1
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EP
European Patent Office
Prior art keywords
rocker
bearing
rocker arm
groove
oil
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EP08018202A
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German (de)
French (fr)
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EP2090757A2 (en
EP2090757A3 (en
Inventor
Werner Vogel
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MAN Truck and Bus SE
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MAN Nutzfahrzeuge AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms

Definitions

  • the invention relates to a rocker arm assembly of an internal combustion engine with a rocker arm and a journal, wherein the bearing pin has a trained as a running surface outer peripheral surface and engages in a bearing shell lined with a central bore of the rocker arm, so that the rocker arm is pivotally mounted on the running surface of the journal, the Bearing journal has a running in its inner first oil passage, which opens in at least one arranged below a central longitudinal axis of the journal outlet opening on the tread, and the fixedly connected to the rocker bearing shell has a hollow cylindrical shape with a shell outer surface and a shell inner surface.
  • the bearing shell which is also referred to as a bearing bush, on its shell inner surface, ie its inner side or its inner, ie the interior of the hollow cylinder facing peripheral surface, inner grooves which are in communication with the first oil passage of the journal.
  • the object of the invention is therefore to provide a rocker arm assembly of the type described, in which a small oil loss occurs.
  • a rocker arm assembly according to the features of claim 1 is given.
  • a lower half of the shell inner surface is provided with at least one inner groove extending in the circumferential direction and ending on both sides below the central longitudinal axis, which extends at least into a region in which the outlet opening of the first oil channel is arranged at a basic position of the rocker arm.
  • the outer shell surface is provided with at least one extending in the circumferential direction, extending to an inlet opening of a rocker arm extending in the second oil groove extending outer groove.
  • the bearing shell has at least one through groove connecting the inner groove and the outer groove.
  • the grooves in the bearing shell extend only partially on the inside thereof. These inner grooves each terminate below the central longitudinal axis, ie below a horizontal plane extending through the central longitudinal axis. They are primarily used to lubricate the tread.
  • Au ⁇ ennuten are also provided in the rocker arm assembly according to the invention, which are in communication with the / the réellenut / s and which are intended to supply oil to the second oil channels connected to the secondary consumers. This division is favorable.
  • the inner and outer grooves can be designed specifically according to their respective function.
  • this measure also has an advantageous effect on the otherwise occurring under load oil loss. Since the internal grooves already end below the central longitudinal axis, the internal grooves are even additionally sealed under load by the bearing journal, which is then pressed more strongly against the lower half of the bearing shell. The larger gap forming under the action of load in the region of the upper half of the bearing shell between the same and the bearing pin does not result in any appreciably increased oil loss in the rocker arm arrangement according to the invention. This area is not supplied with oil in contrast to the prior art. The inner grooves end before, so still in the lower half.
  • the outer grooves which may in particular extend into this region of the upper half of the central bore of the rocker arm, to feed the well disposed there inlet openings of the second oil channels with oil, are due to the in this area in particular unbroken wall of the bearing shell of the under load enlarged gap separated.
  • the same advantageous oil-saving behavior results when the bearing clearance during runtime, e.g. due to aging, enlarged.
  • the first oil passage has a bearing pin completely penetrating and extending below the central longitudinal axis transverse bore. This results in two outlets communicating with the inner groove (s) on the tread, thus providing an improved oil supply to the inner groove (s).
  • the inlet opening is located above the central longitudinal axis in an inner wall of the central bore of the rocker arm, and the outer groove begins below the central longitudinal axis and ends above the central longitudinal axis, wherein it extends at least up to the inlet opening.
  • the outer groove begins below the central longitudinal axis and ends above the central longitudinal axis, wherein it extends at least up to the inlet opening.
  • At least two second oil passages are preferably arranged in the rocker arm and the shell outer surface is provided with at least two outer grooves, each outer groove being associated with only one of the inlet openings of the second oil passages.
  • the oil supply can be adjusted specifically to the respective oil demand of the secondary consumers connected to the second oil channels.
  • the outer grooves have at least partially different groove geometries, in particular different groove depths and / or different groove widths. Even so, the oil throughput in each outer groove can be set according to the specific needs.
  • the passage opening in the bearing shell is arranged in the region in which the outlet opening of the first oil channel is at a basic position of the rocker arm. This results in the best or at least a very good supply of oil to the secondary consumers. The oil can then pass directly from the first oil passage in the outer grooves, ie in particular without much detour within the réellenut / s.
  • the inner groove and the outer groove are each formed as embossing groove.
  • embossed on both sides can be produced well and inexpensively.
  • no additional expenditure is incurred by the additional outer grooves, that is to say by the embossing provided on both sides.
  • Fig. 1 and 2 is an embodiment of a rocker arm assembly 1 shown in detail not shown with internal combustion engine. It comprises a rocker arm 2 with a central bore 3 and a bearing journal 4, whose outer peripheral surface is a bearing or running surface 5, on which the rocker arm 2 is mounted navschwenkbar means of a bearing shell 6.
  • the bearing shell 6 is pressed into the central bore 3 of the rocker arm 2, so that a solid mechanical connection between these two components results.
  • the bearing pin 4 engages with its running surface 5 in the bearing shell 6, wherein the bearing shell 6 is pivotally mounted about a central longitudinal axis 7 of the bearing journal 4 on the bearing journal 4.
  • journal 4 Within the journal 4 extends in the axial direction, ie in the direction of the central longitudinal axis 7, eccentrically and in the lower half of the journal 4, an oil longitudinal channel 8, from which an oil cross channel 9 branches off in the direction of the tread 5 at the level of the rocker arm 2.
  • the oil transverse channel 9 is designed as a transverse bore, which completely penetrates the bearing journal 4 and opens on the running surface 5 into two outlet openings 10 and 11.
  • the oil transverse channel 9 runs like the oil longitudinal channel 8 below the central longitudinal axis 7, or below a central longitudinal axis. 7 comprehensive horizontal plane.
  • the two outlet openings 10 and 11 are located in the lower half of the journal. 4
  • the rocker arm 2 has two lever arms 12 and 13, one of which is mechanically connected by means of a pressed-in this lever arm 12 ball pressure piece 14 and a push rod 15 with a camshaft not shown in detail, whereas the other lever arm 13 is in mechanical contact with a valve bridge 16.
  • a valve bridge 16 By means of the valve bridge 16, two cylinder valves, also not shown in detail, of the internal combustion engine can be actuated.
  • each of the lever arms 12 and 13 each have an oil passage 17 and 18, which supplies the valve bridge 16 and the possibly hydraulically operated components connected thereto or the ball pressure piece 14 as oil secondary consumers with oil.
  • the oil passages 17 and 18 each have one in the upper half of the central bore 3 of the rocker arm 2, ie above the central longitudinal axis 7, arranged in an inner wall of the central bore 3 inlet opening 19 and 20th
  • the bearing shell 6 fixedly connected to the rocker arm 2 is designed as a hollow cylinder having on the outer side a shell outer surface 21 which forms the outer peripheral surface of the hollow cylinder and on the inside of a shell inner surface 22, which is the inner, i. the inner space of the hollow cylinder facing peripheral surface forms, has.
  • the shell outer surface 21 of the bearing shell 6 is due to the press connection directly and closely against the inner wall of the central bore 3 of the rocker arm 2.
  • the shell inner surface 22 is provided in its lower half with an inner groove 23 ending on both sides below the central longitudinal axis 7, ie, in turn, below the horizontal plane passing through the central longitudinal axis 7. It runs in the circumferential direction and extends at the in Fig. 1 and 2 shown basic position of the rocker arm 2 at both ends to slightly beyond the respective outlet opening 10 and 11 of the oil transverse channel 9 addition.
  • the oil cross channel 9 is connected by means of its two outlet openings 10 and 11 with this inner groove 23 in connection and feeds the latter at least in the basic position of the rocker arm 2 on both sides with oil.
  • This Basic position in which the push rod rests against the cam base circle of the camshaft and the valves which can be actuated via the valve bridge 16 are closed. Both exit openings 10 and 11 border the inner groove 23.
  • the shell outer surface 21 is provided with two outer grooves 24 and 25, which also extend in the circumferential direction. They each begin in the lower half of the central bore 3 and extend in the upper half of the central bore 3 to slightly above each one of the inlet openings 19 and 20 also.
  • Each of the oil channels 17 and 18 is connected by means of its inlet opening 19 or 20 with one of the outer grooves 24 and 25 in connection.
  • Each of the outer grooves 24 and 25 feeds its associated oil passage 17 and 18 with oil.
  • the inner groove 23 is connected to each of the two outer grooves 24 and 25.
  • a passage opening 26 or 27 designed as a through-bore is provided in each case in the bearing shell 6.
  • Each of the passage openings 26 and 27 is located opposite one of the two outlet openings 10 and 11 of the oil transverse channel 9 when the rocker arm 2 is in the home position.
  • the oil supplied via the oil cross channel 9 is required firstly for lubricating the running surface 5 and secondly for supplying the auxiliary consumers connected to the oil passages 17 and 18.
  • substantially separate structural means are provided in the rocker arm assembly 1.
  • a corresponding partial flow of oil, which leads directly from the outlet openings 10 and 11 in the inner groove 23 is denoted by 28.
  • the outer grooves 24 and 25 are provided for oil supply to the secondary consumers.
  • a belonging thereto partial oil flow, from the outlet opening 10 and 11, via the passage opening 26 and 27, the outer groove 24 and 25, the inlet opening 19 and 20 in the oil passage 17 and 18 leads, is denoted by 29 and 30, respectively.
  • the oil flow rate for the oil supply of the secondary consumers can be adjusted in each of the outer grooves 24 and 25 specifically to the respective requirements of each connected auxiliary consumers on the individually predetermined groove geometry, eg the respective groove depth or groove width. Both outer grooves 24 and 25 may thus have different geometry parameters.
  • the grooves 23 to 25 provided on the inside and outside of the bearing shell 6 in the rocker arm assembly 1, and in particular their special geometric arrangement, have a favorable effect on operating situations during which the bearing journal 4 is locked, e.g. moved under the action of a load in the direction of arrow 31. Then it comes in the region of the upper half of the bearing pin 4 to form a gap 32 between the tread 5 and the shell inner surface 22 of the bearing shell 6. Such a gap may also form due to an increase in the bearing clearance in the course of service life. In conventional rocker arm arrangements such a gap leads to an oil loss, which must be compensated by an appropriately sized oil supply.
  • the rocker arm assembly 1, however, is designed so that such oil loss does not occur or at least not to a significant extent.
  • the journal 4 moves in the direction of the arrow 31, it comes to lateral areas 33 and 34 of the tread 5, which are approximately at the height of the central longitudinal axis 7, but in any case above the two upper ends of the inner groove 23, to a seal the inner groove 23 opposite to the gap 32 forming in the upper half.
  • an axial oil outlet at this gap 32 is prevented.
  • both the oil supply to the tread 5 by means of the then specially sealed inner groove 23 and the oil supply to the auxiliary consumers by means of the outer grooves 24 and 25 remains unchanged.
  • the rocker arm assembly 1 thus characterized by an extremely low oil loss, in particular at a load on the bearing journal 4, but also in any other conditional bearing play enlargement.

Description

Die Erfindung betrifft eine Kipphebelanordnung einer Brennkraftmaschine mit einem Kippelhebel und einem Lagerzapfen, wobei der Lagerzapfen eine als Lauffläche ausgebildete äußere Umfangsfläche aufweist und in eine mit einer Lagerschale ausgekleidete Zentralbohrung des Kipphebels eingreift, so dass der Kipphebel schwenkbar auf der Lauffläche des Lagerzapfens gelagert ist, der Lagerzapfen einen in seinem Inneren verlaufenden ersten Ölkanal hat, der in mindestens einer unterhalb einer Mittenlängsachse des Lagerzapfens angeordneten Austrittsöffnung an der Lauffläche mündet, und die fest mit dem Kipphebel verbundene Lagerschale eine hohlzylindrische Form mit einer Schalenaußenfläche und einer Schaleninnenfläche hat.The invention relates to a rocker arm assembly of an internal combustion engine with a rocker arm and a journal, wherein the bearing pin has a trained as a running surface outer peripheral surface and engages in a bearing shell lined with a central bore of the rocker arm, so that the rocker arm is pivotally mounted on the running surface of the journal, the Bearing journal has a running in its inner first oil passage, which opens in at least one arranged below a central longitudinal axis of the journal outlet opening on the tread, and the fixedly connected to the rocker bearing shell has a hollow cylindrical shape with a shell outer surface and a shell inner surface.

Bei derzeit gängigen derartigen Kipphebelanordnungen wie z.B. aus EP-A-0 023 250 bekannt, weist die Lagerschale, die auch als Lagerbuchse bezeichnet wird, an ihrer Schaleninnenfläche, also ihrer Innenseite bzw. ihrer inneren, d.h. dem Innenraum des Hohlzylinders zugewandten Umfangsfläche, Innennuten auf, die mit dem ersten Ölkanal des Lagerzapfens in Verbindung stehen. Mittels dieser innen an der Lagerschale angeordneten Nuten erfolgt sowohl die Schmierung der Lauffläche als auch die Verteilung des Hydrauliköls zu zweiten Ölkanälen, die innerhalb des Kipphebels verlaufen und das Hydrauliköl zu Nebenverbrauchern führen. Bei letzteren handelt es sich z.B. um die Kontaktsstelle zwischen dem im Kipphebel montierten Kugeldruckstück und der Stößelstange und/oder um die Komponenten der bei der Brennkraftmaschine zumindest teilweise in den Verbindungsmechanismus zwischen der Nockenwelle und den Auslassventilen mit eingebauten Motorbremseinrichtung (= EVB (= Exhaust Valve Break)).In currently common such Kipphebelanordnungen such as out EP-A-0 023 250 known, the bearing shell, which is also referred to as a bearing bush, on its shell inner surface, ie its inner side or its inner, ie the interior of the hollow cylinder facing peripheral surface, inner grooves which are in communication with the first oil passage of the journal. By means of these grooves arranged inside the bearing shell, both the lubrication of the running surface and the distribution of the hydraulic oil to second oil passages, which run inside the rocker arm and lead the hydraulic oil to secondary consumers, take place. The latter is, for example, the contact point between the ball pressure piece mounted in the rocker arm and the push rod and / or the components of the internal combustion engine at least partially in the connection mechanism between the camshaft and the exhaust valves with built-in engine brake device (= EVB = Exhaust Valve Break )).

Bei einer Spielvergrößerung und/oder unter Last bildet sich im von der Last abgewandten Bereich der Lagerung, d.h. im Bereich der oberen Hälfte der Lagerschale, ein größerer Spalt zwischen der Lagerschale und der Lauffläche des Lagerzapfens. Dieser vergrößerte Spalt führt in Verbindung mit den Innennuten bei den gängigen Kipphebelanordnungen zu einem axialen Ölverlust.At a game magnification and / or under load is formed in the area facing away from the load of storage, i. in the area of the upper half of the bearing shell, a larger gap between the bearing shell and the bearing surface of the journal. This enlarged gap, in conjunction with the internal grooves in the common rocker arm arrangements, results in axial oil loss.

Die Aufgabe der Erfindung besteht nun darin, eine Kipphebelanordnung der eingangs bezeichneten Art anzugeben, bei der ein geringer Ölverlust auftritt.The object of the invention is therefore to provide a rocker arm assembly of the type described, in which a small oil loss occurs.

Zur Lösung dieser Aufgabe wird eine Kipphebelanordnung entsprechend den Merkmalen des Patentanspruchs 1 angegeben. Bei der erfindungsgemäßen Kipphebelanordnung ist eine untere Hälfte der Schaleninnenfläche mit mindestens einer in Umfangsrichtung verlaufenden und beidseitig unterhalb der Mittenlängsachse endenden Innennut versehen, die sich zumindest bis in einen Bereich erstreckt, in dem die Austrittsöffnung des ersten Ölkanals bei einer Grundstellung des Kipphebels angeordnet ist. Weiterhin ist die Schalenaußenfläche mit mindestens einer in Umfangsrichtung verlaufenden, sich bis zu einer Eintrittsöffnung eines im Kipphebel verlaufenden zweiten Ölkanals erstreckenden Außennut versehen. Die Lagerschale hat mindestens eine die Innennut und die Außennut miteinander verbindende Durchgangsöffnung.To solve this problem, a rocker arm assembly according to the features of claim 1 is given. In the rocker arm arrangement according to the invention, a lower half of the shell inner surface is provided with at least one inner groove extending in the circumferential direction and ending on both sides below the central longitudinal axis, which extends at least into a region in which the outlet opening of the first oil channel is arranged at a basic position of the rocker arm. Furthermore, the outer shell surface is provided with at least one extending in the circumferential direction, extending to an inlet opening of a rocker arm extending in the second oil groove extending outer groove. The bearing shell has at least one through groove connecting the inner groove and the outer groove.

Bei der erfindungsgemäßen Kipphebelanordnung verlaufen die Nuten in der Lagerschale nur teilweise an deren Innenseite. Diese Innennuten enden jeweils unterhalb der Mittenlängsachse, d.h. unterhalb einer durch die Mittellängsachse verlaufenden Horizontalebene. Sie dienen in erster Linie zur Schmierung der Lauffläche. Daneben sind bei der erfindungsgemäßen Kipphebelanordnung zusätzlich auch Auβennuten vorgesehen, die mit der/den Innennut/en in Verbindung stehen und die zur Ölversorgung der an die zweiten Ölkanäle angeschlossenen Nebenverbraucher bestimmt sind. Diese Aufteilung ist günstig. So können die Innen- und Außennuten entsprechend ihrer jeweiligen Funktion gezielt ausgelegt werden.In the rocker arm assembly according to the invention, the grooves in the bearing shell extend only partially on the inside thereof. These inner grooves each terminate below the central longitudinal axis, ie below a horizontal plane extending through the central longitudinal axis. They are primarily used to lubricate the tread. In addition, Auβennuten are also provided in the rocker arm assembly according to the invention, which are in communication with the / the Innennut / s and which are intended to supply oil to the second oil channels connected to the secondary consumers. This division is favorable. Thus, the inner and outer grooves can be designed specifically according to their respective function.

Außerdem wirkt sich diese Maßnahme auch vorteilhaft bezüglich des ansonsten unter Last auftretenden Ölverlusts aus. Da die Innennuten bereits unterhalb der Mittenlängsachse enden, werden die Innennuten unter Lasteinwirkung durch den dann stärker gegen die untere Hälfte der Lagerschale gepressten Lagerzapfen sogar zusätzlich abgedichtet. Der sich unter Lasteinwirkung im Bereich der oberen Hälfte der Lagerschale zwischen derselben und dem Lagerzapfen ausbildende größere Spalt führt bei der erfindungsgemäßen Kipphebelanordnung zu keinem nennenswert erhöhten Ölverlust. Dieser Bereich wird im Unterschied zum Stand der Technik nicht mit Öl versorgt. Die Innennuten enden vorher, also noch in der unteren Hälfte. Die Außennuten, die sich insbesondere bis in diesen Bereich der oberen Hälfte der Zentralbohrung des Kipphebels erstrecken können, um die durchaus auch dort angeordneten Eintrittsöffnungen der zweiten Ölkanäle mit Öl zu speisen, sind aufgrund der in diesem Bereich insbesondere undurchbrochenen Wand der Lagerschale von dem unter Last vergrößerten Spalt getrennt. Das gleiche vorteilhafte ölsparende Verhalten ergibt sich, wenn sich das Lagerspiel während der Laufzeit, z.B. aufgrund von Alterungserscheinungen, vergrößert.In addition, this measure also has an advantageous effect on the otherwise occurring under load oil loss. Since the internal grooves already end below the central longitudinal axis, the internal grooves are even additionally sealed under load by the bearing journal, which is then pressed more strongly against the lower half of the bearing shell. The larger gap forming under the action of load in the region of the upper half of the bearing shell between the same and the bearing pin does not result in any appreciably increased oil loss in the rocker arm arrangement according to the invention. This area is not supplied with oil in contrast to the prior art. The inner grooves end before, so still in the lower half. The outer grooves, which may in particular extend into this region of the upper half of the central bore of the rocker arm, to feed the well disposed there inlet openings of the second oil channels with oil, are due to the in this area in particular unbroken wall of the bearing shell of the under load enlarged gap separated. The same advantageous oil-saving behavior results when the bearing clearance during runtime, e.g. due to aging, enlarged.

Vorteilhafte Ausgestaltungen der erfindungsgemäßen Kipphebelanordnung ergeben sich aus den Merkmalen der von Anspruch 1 abhängigen Ansprüche.Advantageous embodiments of the rocker arm assembly according to the invention will become apparent from the features of the dependent claims of claim 1.

Günstig ist eine Variante, bei der der erste Ölkanal eine den Lagerzapfen vollständig durchdringende und unterhalb der Mittenlängsachse verlaufende Querbohrung aufweist. Dadurch resultieren zwei mit der/den Innennut/en in Verbindung stehende Austrittsöffnungen an der Lauffläche, so dass eine verbesserte Ölzufuhr in die Innennut/en gegeben ist.Conveniently, a variant in which the first oil passage has a bearing pin completely penetrating and extending below the central longitudinal axis transverse bore. This results in two outlets communicating with the inner groove (s) on the tread, thus providing an improved oil supply to the inner groove (s).

Gemäß einer anderen vorteilhaften Variante ist es vorgesehen, dass sich die Eintrittsöffnung oberhalb der Mittenlängsachse in einer Innenwand der Zentralbohrung des Kipphebels befindet, und die Außennut unterhalb der Mittenlängsachse beginnt und oberhalb der Mittenlängsachse endet, wobei sie sich mindestens bis zu der Eintrittsöffnung erstreckt. In dieser Konstellation kommen die durch die Trennung in Innen- und Außennut bedingten, vorstehend genannten Vorteile besonders gut zur Geltung.According to another advantageous variant, it is provided that the inlet opening is located above the central longitudinal axis in an inner wall of the central bore of the rocker arm, and the outer groove begins below the central longitudinal axis and ends above the central longitudinal axis, wherein it extends at least up to the inlet opening. In this constellation come by the separation in Inner and outer groove conditional, the advantages mentioned above particularly well.

Vorzugsweise sind im Kipphebel außerdem mindestens zwei zweite Ölkanäle angeordnet und die Schalenaußenfläche ist mit mindestens zwei Außennuten versehen, wobei jede Außennut nur einer der Eintrittsöffnungen der zweiten Ölkanäle zugeordnet ist. Damit kann die Ölversorgung gezielt an den jeweiligen Ölbedarf der an die zweiten Ölkanäle angeschlossenen Nebenverbraucher angepasst werden.In addition, at least two second oil passages are preferably arranged in the rocker arm and the shell outer surface is provided with at least two outer grooves, each outer groove being associated with only one of the inlet openings of the second oil passages. Thus, the oil supply can be adjusted specifically to the respective oil demand of the secondary consumers connected to the second oil channels.

Gleiches gilt auch für die weitere bevorzugte Ausgestaltung, gemäß der die Außennuten zumindest teilweise unterschiedliche Nutgeometrien, insbesondere unterschiedliche Nuttiefen und/oder unterschiedliche Nutbreiten haben. Auch so lässt sich der Öldurchsatz in jeder Außennut gezielt entsprechend der jeweiligen Bedürfnisse einstellen.The same applies to the further preferred embodiment, according to which the outer grooves have at least partially different groove geometries, in particular different groove depths and / or different groove widths. Even so, the oil throughput in each outer groove can be set according to the specific needs.

Günstig ist weiterhin eine Variante, bei der die Durchgangsöffnung in der Lagerschale in dem Bereich angeordnet ist, in dem sich die Austrittsöffnung des
ersten Ölkanals bei einer Grundstellung des Kipphebels befindet. So ergibt sich die beste oder zumindest eine sehr gute Ölversorgung der Nebenverbraucher. Das Öl kann dann direkt vom ersten Ölkanal in die Außennuten gelangen, d.h. insbesondere ohne größeren Umweg innerhalb der Innennut/en.Also favorable is a variant in which the passage opening in the bearing shell is arranged in the region in which the outlet opening of the
first oil channel is at a basic position of the rocker arm. This results in the best or at least a very good supply of oil to the secondary consumers. The oil can then pass directly from the first oil passage in the outer grooves, ie in particular without much detour within the Innennut / s.

Weiterhin ist es vorzugsweise vorgesehen, dass die Innennut und die Außennut jeweils als Prägenut ausgebildet sind. Eine solche dann beidseitig geprägte Lagerschale lässt sich gut und kostengünstig herstellen. Bei einer üblicherweise ohnehin mittels Prägens und/oder Rollens hergestellten Lagerschale entsteht durch die zusätzlichen äußeren Nuten, also durch die dann beidseitig vorgesehene Prägung, kein wesentlicher Mehraufwand.Furthermore, it is preferably provided that the inner groove and the outer groove are each formed as embossing groove. Such a bearing shell embossed on both sides can be produced well and inexpensively. In a bearing shell, which is usually produced anyway by means of embossing and / or rolling, no additional expenditure is incurred by the additional outer grooves, that is to say by the embossing provided on both sides.

Weitere Merkmale, Vorteile und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines Ausführungsbeispiels anhand der Zeichnung. Es zeigt:

Fig. 1
ein Ausführungsbeispiel einer Kipphebelanordnung einer Brennkraftma- schine mit einer Lagerschale, die an der Innen- und an der Außenseite öl- führende Nuten aufweist, und
Fig. 2
einen vergrößerten, die Kipphebellagerung zeigenden Ausschnitt der Kipp- hebelanordnung gemäß Fig.1.
Further features, advantages and details of the invention will become apparent from the following description of an embodiment with reference to the drawing. It shows:
Fig. 1
an embodiment of a rocker arm assembly of an internal combustion engine with a bearing shell having on the inside and on the outside oil-leading grooves, and
Fig. 2
an enlarged, the rocker arm bearing pointing section of the tilt lever assembly according to Fig.1 ,

Einander entsprechende Teile sind in den Fig. 1 und 2 mit denselben Bezugszeichen versehen.Corresponding parts are in the Fig. 1 and 2 provided with the same reference numerals.

In Fig. 1 und 2 ist ein Ausführungsbeispiel einer Kipphebelanordnung 1 einer im Detail nicht mit dargestellten Brennkraftmaschine gezeigt. Sie umfasst einen Kipphebel 2 mit einer Zentralbohrung 3 sowie einen Lagerzapfen 4, dessen äußere Umfangsfläche eine Lager- bzw. Lauffläche 5 darstellt, auf der der Kipphebel 2 mittels einer Lagerschale 6 drehschwenkbar gelagert ist. Die Lagerschale 6 ist dazu in die Zentralbohrung 3 des Kipphebels 2 eingepresst, so dass eine feste mechanische Verbindung zwischen diesen beiden Bauteilen resultiert. Der Lagerzapfen 4 greift mit seiner Lauffläche 5 in die Lagerschale 6 ein, wobei die Lagerschale 6 um eine Mittenlängsachse 7 des Lagerzapfens 4 drehschwenkbar auf dem Lagerzapfen 4 sitzt.In Fig. 1 and 2 is an embodiment of a rocker arm assembly 1 shown in detail not shown with internal combustion engine. It comprises a rocker arm 2 with a central bore 3 and a bearing journal 4, whose outer peripheral surface is a bearing or running surface 5, on which the rocker arm 2 is mounted drehschwenkbar means of a bearing shell 6. The bearing shell 6 is pressed into the central bore 3 of the rocker arm 2, so that a solid mechanical connection between these two components results. The bearing pin 4 engages with its running surface 5 in the bearing shell 6, wherein the bearing shell 6 is pivotally mounted about a central longitudinal axis 7 of the bearing journal 4 on the bearing journal 4.

Innerhalb des Lagerzapfens 4 verläuft in axialer Richtung, d.h. in Richtung der Mittenlängsachse 7, außermittig und in der unteren Hälfte des Lagerzapfens 4 ein Öllängskanal 8, von dem in Höhe des Kipphebels 2 ein Ölquerkanal 9 in Richtung der Lauffläche 5 abzweigt. Der Ölquerkanal 9 ist als eine Querbohrung ausgeführt, die den Lagerzapfen 4 vollständig durchdringt und an der Lauffläche 5 in zwei Austrittsöffnungen 10 und 11 mündet. Der Ölquerkanal 9 verläuft wie der Öllängskanal 8 unterhalb der Mittenlängsachse 7, bzw. unterhalb einer die Mittellängsachse 7 umfassenden Horizontalebene. Auch die beiden Austrittsöffnungen 10 und 11 befinden sich in der unteren Hälfte des Lagerzapfens 4.Within the journal 4 extends in the axial direction, ie in the direction of the central longitudinal axis 7, eccentrically and in the lower half of the journal 4, an oil longitudinal channel 8, from which an oil cross channel 9 branches off in the direction of the tread 5 at the level of the rocker arm 2. The oil transverse channel 9 is designed as a transverse bore, which completely penetrates the bearing journal 4 and opens on the running surface 5 into two outlet openings 10 and 11. The oil transverse channel 9 runs like the oil longitudinal channel 8 below the central longitudinal axis 7, or below a central longitudinal axis. 7 comprehensive horizontal plane. The two outlet openings 10 and 11 are located in the lower half of the journal. 4

Der Kipphebel 2 hat zwei Hebelarme 12 und 13, von denen einer mittels eines in diesen Hebelarm 12 eingepressten Kugeldruckstücks 14 und einer Stößelstange 15 mit einer nicht näher gezeigten Nockenwelle mechanisch verbunden ist, wohingegen der andere Hebelarm 13 mit einer Ventilbrücke 16 in mechanischem Kontakt steht. Mittels der Ventilbrücke 16 können zwei ebenfalls nicht näher gezeigte Zylinderventile der Brennkraftmaschine betätigt werden. In jedem der Hebelarme 12 und 13 verläuft jeweils ein Ölkanal 17 bzw. 18, der die Ventilbrücke 16 und die ggf. daran angeschlossenen hydraulisch betriebenen Komponenten bzw. das Kugeldruckstück 14 als Ölnebenverbraucher mit Öl versorgt. Die Ölkanäle 17 und 18 haben jeweils eine in der oberen Hälfte der Zentralbohrung 3 des Kipphebels 2, also oberhalb der Mittenlängsachse 7, in einer Innenwand der Zentralbohrung 3 angeordnete Eintrittsöffnung 19 bzw. 20.The rocker arm 2 has two lever arms 12 and 13, one of which is mechanically connected by means of a pressed-in this lever arm 12 ball pressure piece 14 and a push rod 15 with a camshaft not shown in detail, whereas the other lever arm 13 is in mechanical contact with a valve bridge 16. By means of the valve bridge 16, two cylinder valves, also not shown in detail, of the internal combustion engine can be actuated. In each of the lever arms 12 and 13 each have an oil passage 17 and 18, which supplies the valve bridge 16 and the possibly hydraulically operated components connected thereto or the ball pressure piece 14 as oil secondary consumers with oil. The oil passages 17 and 18 each have one in the upper half of the central bore 3 of the rocker arm 2, ie above the central longitudinal axis 7, arranged in an inner wall of the central bore 3 inlet opening 19 and 20th

Die fest mit dem Kipphebel 2 verbundene Lagerschale 6 ist als Hohlzylinder ausgeführt, der an der Außenseite eine Schalenaußenfläche 21, die die äußere Umfangsfläche des Hohlzylinders bildet, und an der Innenseite einer Schaleninnenfläche 22, die die innere, d.h. dem Innenraum des Hohlzylinders zugewandte Umfangsfläche bildet, aufweist. Im montierten Zustand liegt die Schalenaußenfläche 21 der Lagerschale 6 aufgrund der Pressverbindung direkt und eng an der Innenwand der Zentralbohrung 3 des Kipphebels 2 an.The bearing shell 6 fixedly connected to the rocker arm 2 is designed as a hollow cylinder having on the outer side a shell outer surface 21 which forms the outer peripheral surface of the hollow cylinder and on the inside of a shell inner surface 22, which is the inner, i. the inner space of the hollow cylinder facing peripheral surface forms, has. In the assembled state, the shell outer surface 21 of the bearing shell 6 is due to the press connection directly and closely against the inner wall of the central bore 3 of the rocker arm 2.

Die Schaleninnenfläche 22 ist in ihrer unteren Hälfte mit einer beidseitig unterhalb der Mittenlängsachse 7, d.h. wiederum unterhalb der durch die Mittellängsachse 7 verlaufenden Horizontalebene, endenden Innennut 23 versehen. Sie verläuft in Umfangsrichtung und erstreckt sich bei der in Fig. 1 und 2 gezeigten Grundstellung des Kipphebels 2 an beiden Enden bis etwas über die jeweilige Austrittsöffnung 10 bzw. 11 des Ölquerkanals 9 hinaus. Der Ölquerkanal 9 steht mittels seiner beiden Austrittsöffnungen 10 und 11 mit dieser Innennut 23 in Verbindung und speist letztere zumindest bei der Grundstellung des Kipphebels 2 beidseitig mit Öl. Bei dieser Grundstellung, bei der die Stößelstange am Nockengrundkreis der Nockenwelle anliegt und die über die Ventilbrücke 16 betätigbaren Ventile geschlossen sind, .grenzen beide Austrittsöffnungen 10 und 11 an die Innennut 23 an.The shell inner surface 22 is provided in its lower half with an inner groove 23 ending on both sides below the central longitudinal axis 7, ie, in turn, below the horizontal plane passing through the central longitudinal axis 7. It runs in the circumferential direction and extends at the in Fig. 1 and 2 shown basic position of the rocker arm 2 at both ends to slightly beyond the respective outlet opening 10 and 11 of the oil transverse channel 9 addition. The oil cross channel 9 is connected by means of its two outlet openings 10 and 11 with this inner groove 23 in connection and feeds the latter at least in the basic position of the rocker arm 2 on both sides with oil. At this Basic position in which the push rod rests against the cam base circle of the camshaft and the valves which can be actuated via the valve bridge 16 are closed. Both exit openings 10 and 11 border the inner groove 23.

Die Schalenaußenfläche 21 ist mit zwei Außennuten 24 und 25 versehen, die ebenfalls in Umfangsrichtung verlaufen. Sie beginnen jeweils in der unteren Hälfte der Zentralbohrung 3 und erstrecken sich in der oberen Hälfte der Zentralbohrung 3 bis etwas über jeweils eine der Eintrittsöffnungen 19 und 20 hinaus. Jeder der Ölkanäle 17 und 18 steht mittels seiner Eintrittsöffnung 19 bzw. 20 mit einer der Außennuten 24 und 25 in Verbindung. Jede der Außennuten 24 und 25 speist den ihr zugeordneten Ölkanal 17 bzw. 18 mit Öl.The shell outer surface 21 is provided with two outer grooves 24 and 25, which also extend in the circumferential direction. They each begin in the lower half of the central bore 3 and extend in the upper half of the central bore 3 to slightly above each one of the inlet openings 19 and 20 also. Each of the oil channels 17 and 18 is connected by means of its inlet opening 19 or 20 with one of the outer grooves 24 and 25 in connection. Each of the outer grooves 24 and 25 feeds its associated oil passage 17 and 18 with oil.

Die Innennut 23 ist mit jeder der beiden Außennuten 24 und 25 verbunden. Hierzu ist in der Lagerschale 6 jeweils eine als Durchgangsbohrung ausgeführte Durchgangsöffnung 26 bzw. 27 vorgesehen. Jede der Durchgangsöffnungen 26 und 27 liegt einer der beiden Austrittsöffnungen 10 und 11 des Ölquerkanals 9 gegenüber, wenn sich der Kipphebel 2 in der Grundstellung befindet.The inner groove 23 is connected to each of the two outer grooves 24 and 25. For this purpose, a passage opening 26 or 27 designed as a through-bore is provided in each case in the bearing shell 6. Each of the passage openings 26 and 27 is located opposite one of the two outlet openings 10 and 11 of the oil transverse channel 9 when the rocker arm 2 is in the home position.

Im Folgenden werden die Wirkungsweise und besondere Vorteile der Kipphebelanordnung 1 näher beschrieben.In the following, the mode of action and special advantages of the rocker arm assembly 1 will be described in more detail.

Das über den Ölquerkanal 9 zugeführte Öl wird zum einen zur Schmierung der Lauffläche 5 und zum anderen zur Speisung der an die Ölkanäle 17 und 18 angeschlossenen Nebenverbraucher benötigt. Für diese beiden Aufgaben sind bei der Kipphebelanordnung 1 im Wesentlichen voneinander getrennte konstruktive Mittel vorgesehen. Die Ölversorgung der Lauffläche 5 erfolgt über die Innennut 23. Ein dementsprechender Teilölfluss, der direkt von den Austrittsöffnungen 10 und 11 in die Innennut 23 führt, ist mit 28 bezeichnet. Dagegen sind die Außennuten 24 und 25 zur Ölversorgung der Nebenverbraucher vorgesehen. Ein hierzu gehöriger Teilölfluss, der von der Austrittsöffnung 10 bzw. 11, über die Durchgangsöffnung 26 bzw. 27, die Außennut 24 bzw. 25, die Eintrittsöffnung 19 bzw. 20 in den Ölkanal 17 bzw. 18. führt, ist mit 29 bzw. 30 bezeichnet. Der Öldurchsatz für die Ölversorgung der Nebenverbraucher lässt sich bei jeder der Außennuten 24 und 25 gezielt an die diesbezüglichen Anforderungen der jeweils angeschlossenen Nebenverbraucher über die individuell vorgebbare Nutgeometrie, z.B. die jeweilige Nuttiefe oder Nutbreite, einstellen. Beide Außennuten 24 und 25 können also voneinander abweichende Geometrieparameter aufweisen.The oil supplied via the oil cross channel 9 is required firstly for lubricating the running surface 5 and secondly for supplying the auxiliary consumers connected to the oil passages 17 and 18. For these two tasks substantially separate structural means are provided in the rocker arm assembly 1. The oil supply to the tread 5 via the inner groove 23. A corresponding partial flow of oil, which leads directly from the outlet openings 10 and 11 in the inner groove 23 is denoted by 28. In contrast, the outer grooves 24 and 25 are provided for oil supply to the secondary consumers. A belonging thereto partial oil flow, from the outlet opening 10 and 11, via the passage opening 26 and 27, the outer groove 24 and 25, the inlet opening 19 and 20 in the oil passage 17 and 18 leads, is denoted by 29 and 30, respectively. The oil flow rate for the oil supply of the secondary consumers can be adjusted in each of the outer grooves 24 and 25 specifically to the respective requirements of each connected auxiliary consumers on the individually predetermined groove geometry, eg the respective groove depth or groove width. Both outer grooves 24 and 25 may thus have different geometry parameters.

Die bei der Kipphebelanordnung 1 sowohl an der Innen- als auch an der Außenseite der Lagerschale 6 vorgesehenen Nuten 23 bis 25 und insbesondere deren spezielle geometrische Anordnung wirken sich günstig auf Betriebssituationen aus, während denen sich der Lagerzapfen 4 z.B. unter Einwirkung einer Last in Richtung des Pfeils 31 bewegt. Dann kommt es im Bereich der oberen Hälfte des Lagerzapfens 4 zur Ausbildung eines Spalts 32 zwischen der Lauffläche 5 und der Schaleninnenfläche 22 der Lagerschale 6. Ein derartiger Spalt kann sich im Laufe der Betriebsdauer auch aufgrund einer Vergrößerung des Lagerspiels bilden. Bei konventionellen Kipphebelanordnungen führt ein derartiger Spalt zu einem Ölverlust, der durch eine entsprechend dimensionierte Ölversorgung ausgeglichen werden muss.The grooves 23 to 25 provided on the inside and outside of the bearing shell 6 in the rocker arm assembly 1, and in particular their special geometric arrangement, have a favorable effect on operating situations during which the bearing journal 4 is locked, e.g. moved under the action of a load in the direction of arrow 31. Then it comes in the region of the upper half of the bearing pin 4 to form a gap 32 between the tread 5 and the shell inner surface 22 of the bearing shell 6. Such a gap may also form due to an increase in the bearing clearance in the course of service life. In conventional rocker arm arrangements such a gap leads to an oil loss, which must be compensated by an appropriately sized oil supply.

Die Kipphebelanordnung 1 ist dagegen so konstruiert, dass ein solcher Ölverlust nicht oder zumindest nicht in nennenswertem Umfang auftritt. Wenn sich der Lagerzapfen 4 in Richtung des Pfeils 31 bewegt, kommt es an seitlichen Bereichen 33 und 34 der Lauffläche 5, die sich in etwa auf Höhe der Mittenlängsachse 7, jedenfalls aber oberhalb der beiden oberen Enden der Innennut 23, befinden, zu einer Abdichtung der Innennut 23 gegenüber dem sich in der oberen Hälfte ausbildenden Spalt 32. Dadurch wird ein axialer Ölaustritt an diesem Spalt 32 verhindert.The rocker arm assembly 1, however, is designed so that such oil loss does not occur or at least not to a significant extent. When the journal 4 moves in the direction of the arrow 31, it comes to lateral areas 33 and 34 of the tread 5, which are approximately at the height of the central longitudinal axis 7, but in any case above the two upper ends of the inner groove 23, to a seal the inner groove 23 opposite to the gap 32 forming in the upper half. As a result, an axial oil outlet at this gap 32 is prevented.

Zugleich bleibt aber sowohl die Ölversorgung der Lauffläche 5 mittels der dann besonders abgedichteten Innennut 23 als auch die Ölversorgung der Nebenverbraucher mittels der Außennuten 24 und 25 unverändert gewährleistet. Die Kipphebelanordnung 1 zeichnet sich also durch einen äußerst geringen Ölverlust aus, insbesondere bei einer Lasteinwirkung auf den Lagerzapfen 4, aber auch bei einer anderweitig bedingten Lagerspielvergrößerung.At the same time, however, both the oil supply to the tread 5 by means of the then specially sealed inner groove 23 and the oil supply to the auxiliary consumers by means of the outer grooves 24 and 25 remains unchanged. The rocker arm assembly 1 thus characterized by an extremely low oil loss, in particular at a load on the bearing journal 4, but also in any other conditional bearing play enlargement.

Claims (7)

  1. A rocker-arm arrangement of an internal combustion engine with a rocker arm (2) and a bearing journal (4), wherein
    a) the bearing journal (4) has an outer peripheral surface forked as a bearing surface (5) and engages in a central bore (3), lined with a bearing shell (6), in the rocker arm (2), so that the rocker arm (2) is mounted pivotably on the bearing surface (5) of the bearing journal (4),
    b) the bearing journal (4) has a first oil duct (8, 9) which runs in its interior, which duct opens into at least one exit opening (10, 11) on the bearing surface (5), which opening is arranged beneath a central longitudinal axis (7) of the bearing journal (4),
    c) the bearing shell (6) which is connected securely to the rocker arm (2) has a hollow-cylindrical shape with an outer shell surface (21) and an inner shell surface (22),
    d) a lower half of the inner shell surface (22) is provided with at least one inner groove (23) which runs in the peripheral direction and ends on both sides beneath the central longitudinal axis (7), which groove extends at least into a region in which the exit opening (10, 11) of the first oil duct (8, 9) is arranged in a basic position of the rocker arm (2),
    e) the outer shell surface (21) is provided with at least one outer groove (24, 25) which runs in the peripheral direction and extends as far as an entry opening (19, 20) of a second oil duct (17, 18) which runs in the rocker arm (2),
    f) the bearing shell (6) has at least one passage opening (26, 27) which connect the inner groove (23) and the outer groove (24, 25) together.
  2. A rocker-arm arrangement according to Claim 1, characterised in that the first oil duct (8, 9) has a transverse bore (9) which penetrates completely through the bering journal and runs beneath the central longitudinal axis (7).
  3. A rocker-arm arrangement according to Claim 1, characterised in that the entry opening (19, 20) is located above the central longitudinal axis (7) in an inner wall of the central bore (3) of the rocker arm (2), and the outer groove (24, 25) begins beneath the central longitudinal axis (7) and ends above the central longitudinal axis (7), extending at least as far as the entry opening (19, 20).
  4. A rocker-arm arrangement according to Claim 1, characterised in that at least two second oil ducts (17, 18) are arranged in the rocker arm (2), and the outer shell surface (21) is provided with at least two outer grooves (24, 25), each outer groove (24, 25) being associated with only one of the entry openings (19, 20) of the second oil ducts (17,18).
  5. A rocker-arm arrangement according to Claim 4, characterised in that the outer grooves (24, 25) at least partially have different groove geometries.
  6. A rocker-arm arrangement according to Claim 1, characterised in that the passage opening (26, 27) is arranged in the region in which the exit opening (10, 11) of the first oil duct (8, 9) is located in a basic position of the rocker arm (2).
  7. A rocker-arm arrangement according to Claim 1, characterised in that the inner groove (23) and the outer groove (24, 25) are each designed as embossed grooves.
EP08018202A 2008-02-14 2008-10-17 Tilt lever assembly with a bearing with slots Active EP2090757B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008009170A DE102008009170A1 (en) 2008-02-14 2008-02-14 Rocker arm assembly with a groove having bearing shell

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EP2090757A2 EP2090757A2 (en) 2009-08-19
EP2090757A3 EP2090757A3 (en) 2009-09-16
EP2090757B1 true EP2090757B1 (en) 2010-07-07

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US (1) US8096274B2 (en)
EP (1) EP2090757B1 (en)
CN (1) CN101509401B (en)
BR (1) BRPI0900176B1 (en)
DE (2) DE102008009170A1 (en)
RU (1) RU2410548C2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201700025353A1 (en) * 2017-03-07 2018-09-07 Gnutti Carlo Spa ENDOTHERMAL MOTOR PUNISHMENT
CN108071432A (en) * 2017-12-12 2018-05-25 安徽华菱汽车有限公司 A kind of engine rocker is as foot
US11905858B2 (en) * 2020-07-14 2024-02-20 Powerhouse Engine Solutions Switzerland IP Holding GmbH Systems and methods for rocker arm lubrication

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB528997A (en) * 1939-05-19 1940-11-12 William Warren Triggs Improvements in levers or rockers, particularly for the valve gear of internal combustion engines
GB667791A (en) * 1948-09-03 1952-03-05 Toledo Stamping And Mfg Compan Improvements in or relating to engine rocker arm assemblies
US2563699A (en) * 1949-11-21 1951-08-07 John R Winter Sr Rocker arm construction
US4132196A (en) * 1975-10-02 1979-01-02 Toledo Stamping & Manufacturing Company Rocker arm
DE2930337A1 (en) * 1979-07-26 1981-02-19 Maschf Augsburg Nuernberg Ag VALVE CONTROL MECHANISM FOR ONE OR EXHAUST VALVES FROM INTERNAL COMBUSTION ENGINES
DE3024306A1 (en) * 1980-06-27 1982-01-21 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Plain bearing for rocking movement - has pockets in bush either side of portion subject to max. load with pressurised oil connections
US6640779B1 (en) * 1999-01-05 2003-11-04 Marimuthu Ramu Thiyagarajan Low cost new internal combustion engine with increased mechanical efficiency, fuel saver and pollution controlled
US6422186B1 (en) * 1999-09-10 2002-07-23 Diesel Engine Retarders, Inc. Lost motion rocker arm system with integrated compression brake
DE102005040649A1 (en) * 2005-08-27 2007-03-01 Schaeffler Kg Rocker arm-valve drive for gas exchange valve of e.g. multi-cylinder internal combustion engine, has force transmission device designed as swing/rocker arm that is rotatably supported on lever axle with pressurizing medium guiding channel

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BRPI0900176B1 (en) 2019-07-02
US8096274B2 (en) 2012-01-17
EP2090757A2 (en) 2009-08-19
US20090205600A1 (en) 2009-08-20
CN101509401A (en) 2009-08-19
DE502008000898D1 (en) 2010-08-19
EP2090757A3 (en) 2009-09-16
DE102008009170A1 (en) 2009-08-20
CN101509401B (en) 2012-09-05
RU2410548C2 (en) 2011-01-27
RU2009105152A (en) 2010-08-20
BRPI0900176A2 (en) 2009-09-29

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