EP1358397B1 - Rocker arm for a valve train in an internal combustion engine with device for independent setting/adjustment of the valve play - Google Patents
Rocker arm for a valve train in an internal combustion engine with device for independent setting/adjustment of the valve play Download PDFInfo
- Publication number
- EP1358397B1 EP1358397B1 EP02715421A EP02715421A EP1358397B1 EP 1358397 B1 EP1358397 B1 EP 1358397B1 EP 02715421 A EP02715421 A EP 02715421A EP 02715421 A EP02715421 A EP 02715421A EP 1358397 B1 EP1358397 B1 EP 1358397B1
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- EP
- European Patent Office
- Prior art keywords
- valve
- rocker arm
- predetermined
- cylinder axis
- hollow cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
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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
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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
- F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
- F01L1/183—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft of the boat type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/34—Lateral camshaft position
Definitions
- the present invention relates to a rocker arm for a valve train of an internal combustion engine for the opening actuation of a valve stem against the spring force of the valve closing valve spring, which is equipped with a mechanical valve lash adjustment.
- a typical internal combustion engine uses an array of valves to control the intake and exhaust of gases into and out of an engine cylinder.
- the opening and closing of a valve is usually carried out electromagnetically or purely mechanically, by the valve stem is actuated by a lever assembly, which in turn is controlled by a driven by the crankshaft of the engine camshaft. It is connected to the generally downward movement of the lever assembly and the associated actuation of the valve stem end lifting the valve head of its valve seat. This movement is counteracted by the restoring force of a correspondingly arranged valve spring, which ensures that the valve head is pulled back into its sealing engagement with the valve seat at a suitable time of the engine cycle.
- valve train and valve stem In order to avoid tolerances in the valvetrain and temperature changes during operation of the internal combustion engine to a hard clash of valvetrain and valve stem and also to ensure the safe closing of the valve, it is known between valve train and valve stem to provide a valve clearance of predetermined (minimum) size. However, this increases during operation of the internal combustion engine due to wear in terms of its size, which leads to undesirable changes in the necessary for the operation of the engine exact valve timing and possibly resulting consequential damage.
- valve clearance must be adjusted / readjusted to a predetermined size after a corresponding period of operation of the internal combustion engine, which is generally associated with considerable costs and longer downtimes.
- this maintenance work requires a corresponding expertise and a certain equipment.
- One way out may be to provide self-acting systems for automatically adjusting / adjusting the valve clearance that are known.
- An automatic hydraulic valve clearance compensation ( DE 2200131 C2 ), in which usually a pressure space between a cylinder and a piston displaceably mounted therein via a check valve with pressure oil is filled, so that the piston, which cooperates with the valve stem end, the valve clearance can compensate at any time.
- the DE 43 39 433 A1 describes a valve lever with a deflection device comprising a two wedge surfaces having Verstellkeil which is arranged between a positionally secured in the valve lever in the adjustment of the Verstellkeiles supporting wedge and a Zustellkeil a valve lever in the direction of the gas exchange valve transversely to the adjustment of the Verstellkeiles valve pressure piece.
- the above-mentioned Ventil mecanicinstellelement is characterized in that it comprises a rotatably mounted in the rocker arm hollow cylinder formed around the hollow cylinder circumference flat surfaces (“sliding block”) and a sliding the sliding block in a predetermined direction of rotation torsion spring. Adjacent flat surfaces are delimited from one another by their surface edges.
- the torsion spring for rotation of the sliding block in a predetermined direction of rotation has a much lower spring force than the valve closing the valve spring, so that the closing of the valve undergoes no impairment by an opposing force component of the spring force of the torsion spring.
- the sliding block is designed so that the flat surfaces formed around the circumference of the hollow cylinder are each arranged parallel to the hollow cylinder axis. This implies that there is a perpendicular to the hollow cylinder axis for each flat surface.
- This solder coincides in its direction with a radial direction of the circular cross sections of the hollow cylinder.
- the solder defines the shortest distance of the flat surface from the hollow cylinder axis by a flat surface on the hollow cylinder axis.
- the flat surfaces have parallel to the hollow cylinder axis (and thus also parallel to each other) surface edges. With respect to the rotation of the sliding block caused by the torsion spring in a predetermined direction, the flat edges parallel to the hollow cylinder axis of each flat surface are to be distinguished into a leading leading surface edge and a trailing surface edge leading thereto.
- the flat surfaces each reach a rotational position for actuating the valve stem.
- the final position of the valve and the corresponding position of the rocker arm results at each rotational position of a flat surface of the difference between the vertical distance of the axis of rotation of the hollow cylinder from the valve stem end and the shortest distance of the flat surface of the cylinder axis, a first predetermined valve clearance.
- the automatic further rotation of the sliding block is prevented by abutment of the associated rear surface edge of the flat surface to the valve stem end in the context of a given valve clearance at each flat surface.
- the spring force of the torsion spring thus results in the application of a rear surface edge against the valve stem end to no rotation of the Sliding block, but to bias the sliding block in the direction of rotation.
- the flat surface tilts in the position for actuating the valve stem due to the caused by the torsion spring system of the associated rear surface edge to the valve stem end.
- this inclination of the flat surfaces is lifted relative to the valve stem ends and the flat surface is then the valve stem end over the entire surface.
- valve lash tends to increase due to wear, so that with sufficient increase in the valve clearance, the rear surface edge of the flat surface in the rotational position for actuating the valve stem, the system against the valve stem end, whereby the automatic rotation of the sliding block due to the spring force of the torsion spring begins.
- the rotation can only be used if the flat surface in the position for actuating the valve stem does not fully lie against the end of the valve stem, i. only when the corresponding enlarged valve clearance in the final position of the valve and the corresponding position of the rocker arm is present.
- the automatic rotation of the sliding block is hindered by abutment of the rear surface edge associated with the flat surface in the position for actuating the valve stem, as long as the valve clearance is a second predetermined valve clearance, that is the difference between the radial distance of the rear surface edge of the flat surface from the cylinder axis and corresponds to the shortest distance of this flat surface from the cylinder axis, not reached.
- a wear of the rear surface edge which is expected in practice, however, shortens the adjustment interval.
- each flat surface passes through the automatic rotation of the sliding block in the rotational position for actuating the valve stem, over Increasing shortest distance of the flat surfaces of the cylinder axis a first predetermined valve clearance on or. be readjusted.
- the sliding block In the basic setting of the sliding block this is adjusted so that the flat surface with the smallest shortest distance from the hollow cylinder axis reaches a rotational position for actuating the valve stem.
- the first predetermined valve clearance is set.
- the rocker arm is designed so that the torsion spring is arranged around the hollow cylinder axis, two-bearing coil spring, which has a fixed bearing on the sliding block and the other fixed bearing on the rocker arm. This simplifies the design, saves space and costs.
- An advantageous embodiment of the invention provides that the rocker arm is equipped with at least four flat surfaces, whereby at least a four times Adjustment / readjustment of the first predetermined valve clearance can be detected.
- the first predetermined valve clearance for each flat surface is the same in its rotational position for actuating the valve stem.
- a multiple readjustment of the valve clearance is achieved to a respective same predetermined value.
- a constant minimum valve clearance can be set for each readjustment stage.
- the second predetermined valve clearance be the same for each flat surface in its rotational position for actuating the valve stem. This ensures that a certain, for each flat surface in the rotational position for actuating the valve stem equal valve clearance is not exceeded. In conjunction with a constant first predetermined valve clearance, the valve clearance can thus be kept within the limits defined by the first and the second predetermined valve clearance.
- the first predetermined valve clearance is in the range of 0.01 mm - 1 mm; this is preferably 0.1 mm.
- the second predetermined valve clearance has a difference to the first predetermined valve clearance, which is in the range of 0.05 mm - 1 mm; this is preferably 0.2 mm.
- An advantageous embodiment of the invention provides that the flat surfaces of the sliding block on both sides be limited by mounted on the hollow cylinder washers. In this way, the sliding block in its rotatable mounting in the rocker arm with respect to its deflection in the direction of the axis of rotation can be easily and simultaneously effectively fixed without affecting the automatic rotation of the sliding block.
- the second predetermined valve clearance of the flat surface with the greatest shortest distance i. that plane surface which engages as the last in the rotational position for actuating the valve stem, is chosen so large that the system of the rear surface edge is ensured for an average operating time of the internal combustion engine.
- the sliding block is made of chilled cast iron, sintered material, cold-formed or extruded steel.
- the present device according to the invention can be produced simply and inexpensively.
- a particular advantage of the invention lies in the fact that it requires very little space and is practically universally applicable.
- already manufactured internal combustion engines that use a rocker arm easily and inexpensively retool by replacing the previously used rocker arm with the rocker arm according to the invention.
- a rocker arm 1 via a sliding block 2 in engagement with the valve stem end of a valve stem 4.
- the valve stem 4 is slidably disposed in a valve stem guide 6.
- the valve stem 4 is urged by a valve spring 8 into a position in which the valve disk 11 comes into sealing engagement with the valve ring 12.
- the valve spring 8 is supported, on the one hand, against the cylinder head 13 and, on the other hand, against a projection 10 fastened to the valve stem.
- the rocker arm 1 is fastened to the engine block via a shaft 3.
- the sliding block 2 is rotatably mounted at one end of the rocker arm 1 in a corresponding recess between washers 7.
- a fixed bearing a torsion spring 5 to Rotation of the sliding block 2 is located at the upper edge of the rocker arm.
- the sliding block 2 In the basic setting of the sliding block 2 is the flat surface of the sliding block with the smallest shortest distance, d. H. the shortest solder of the respective flat surface on the hollow cylinder axis, in engagement with the valve stem end. Between each flat surface in the rotational position for actuating the valve stem end and the valve stem is in the final position of the valve and the corresponding position of the rocker arm 1 before the valve clearance. Due to the over the spring force of the torsion spring 5 caused automatic rotation of the sliding block 2, the located in the actuating position flat surface tilts to the valve stem end.
- valve stem 4 follows this movement due to the Spring force of the valve spring 8, without losing the engagement with the flat surface of the sliding block 2.
- the flat surface remains in engagement with the valve stem end, as long as in the direction of rotation of the sliding block 2 after hurrying back surface edge abuts against the valve stem end.
- the sliding block 2 is merely biased by the torsion spring 5 in this state.
- valve clearance As the valve clearance increases over the life of the engine, the valve clearance may become so great as to reach the value of the second predetermined valve clearance where the rear surface edge is no longer against the valve stem end.
- the sliding block is then rotated due to the biasing spring force of the torsion spring until the next flat surface passes through their rear surface edge resting in the rotational position for actuating the valve stem.
- the originally enlarged valve clearance is reduced again by the comparatively larger shortest distance of the flat surface and adjusted to the first predetermined valve clearance.
- valve clearance for example, reaches the value 0.3 mm
- the sliding block rotates to the next surface level and you immediately get back to the output valve clearance, for example, 0.1 mm. It is thus ensured that always a minimum valve clearance is present and the valves do not remain open.
- the Fig. 2a and 2 B each show a top view of the equipped with the sliding block 2 rocker arm 1. It is apparent that the torsion spring 5 configured as a centrally disposed coil spring, which has a fixed bearing on the sliding block 2 and the other fixed bearing in a clasp of the rocker arm 1.
- the sliding block 2 has the shape of a hollow cylinder with trained around its circumference flat surfaces.
- the torsion spring 5 is arranged in the hollow center of the hollow cylinder.
- For fitting in its rotatable mounting of the sliding block is further equipped with two arranged on both sides of the flat surfaces washers 7.
- Fig. 3 the sliding block 2 is shown in cross-section.
- the direction of the rotation of the sliding block caused by the torsion spring 5 is indicated by the arrow.
- the hollow cylinder of the sliding block has the radius R 1 in its circular cross section.
- the flat surfaces also shown in section are formed.
- the intersecting lines of the flat surfaces form a closed polygon around the circumference of the hollow cylinder, which, contrary to the predetermined direction of rotation, always distances further from the peripheral surface.
- Only the cutting line with the shortest vertical radial distance from the axis of rotation touches the peripheral surface of the hollow cylinder.
- This cutting line or the corresponding flat surface of the sliding block is set in the initial basic setting of the sliding block for actuating the valve stem end.
- the vertical radial distance the line of intersection of the hollow cylinder axis corresponds to the perpendicular of the flat surface on the hollow cylinder axis.
- the first predetermined valve clearance results from the difference between the vertical distance of the axis of rotation of the hollow cylinder from the valve stem end and the shortest distance of the flat surface from the cylinder axis. In the basic setting of the sliding block, the first predetermined valve clearance thus lies within the difference between R 1 and R 1 + x 1 .
- the second predetermined valve clearance corresponds to the difference between the radial distance of the rear surface edge of the flat surface from the cylinder axis and the shortest distance of the flat surface from the cylinder axis. In the basic setting of the sliding block, the second predetermined valve clearance is thus x 1 .
- the sliding block jumps over to the next detent position, at which point the next flat surface in the direction opposite to the direction of rotation comes into engagement with the valve stem end.
- the second predetermined valve clearance is x 2 .
- the second predetermined valve clearance is x 3 .
- the sliding block jumps over to the next locking position, at which point the next flat surface, which is opposite in direction to the direction of rotation, engages the valve stem end.
- the number of stages can be selected as needed. For example, wear of 1 mm can be easily compensated. In FIG. 3 By way of example, 7 steps or edges are shown.
- Fig. 4 shows a second example of the sliding block according to the invention with nine flat surfaces.
- the first and second predetermined valve clearances are the same for each flat surface.
- the first predetermined valve clearance is 0.1 mm.
- a valve clearance of 0.1 mm is set.
- the second predetermined valve clearance is 0.3 mm.
- the difference between the second predetermined valve clearance and the first predetermined valve clearance is 0.2 mm.
- Each flat surface snaps into the rotational position to actuate the valve stem after 0.2 mm of wear and reduces the actual valve clearance from 0.3 mm back to 0.1 mm.
- the angles between the adjacent solders are indicated by the flat surfaces on the hollow cylinder axis.
- the hollow cylinder has a length of 14.4 mm, an outer diameter of 7 mm and an inner diameter of 3.7 mm.
- the flat surfaces have a width along the hollow cylinder axis of 6 mm.
- the length of the hollow cylinder on both sides of the area occupied by flat surfaces is 4.2 mm in each case.
- an average service life of 5000 hours can be achieved until the last flat surface engages in the rotational position for actuating the valve stem.
- the back Surface edge of the last flat surface is designed so that during the still following average operating time of the internal combustion engine, the actuation of the valve stem takes place only through the last flat surface.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
Die vorliegende Erfindung betrifft einen Kipphebel für einen Ventiltrieb eines Verbrennungsmotors zur öffnenden Betätigung eines Ventilschaftes entgegen der Federkraft einer das Ventil schließenden Ventilfeder, welcher mit einem mechanischen Ventilspieleinstellelement ausgestattet ist.The present invention relates to a rocker arm for a valve train of an internal combustion engine for the opening actuation of a valve stem against the spring force of the valve closing valve spring, which is equipped with a mechanical valve lash adjustment.
Ein typischer Verbrennungsmotor verwendet eine Anordnung von Ventilen um das Ansaugen und Ablassen von Gasen in und aus einem Motorzylinder zu steuern. Das Öffnen und Schließen eines Ventils erfolgt üblicherweise elektromagnetisch oder rein mechanisch, indem der Ventilschaft über eine Hebelanordnung betätigt wird, die ihrerseits von einer von der Kurbelwelle des Motors angetriebenen Nockenwelle gesteuert wird. Dabei ist mit der in der Regel abwärts gerichteten Bewegung der Hebelanordnung und der damit verbundenen Betätigung des Ventilschaftendes ein Abheben des Ventilkopfes von seinem Ventilsitz verbunden. Dieser Bewegung steht die rückstellende Kraft einer entsprechend angeordneten Ventilfeder entgegen, die dafür sorgt, dass der Ventilkopf zu einem geeigneten Zeitpunkt des Motorzyklus wieder zurück in seinen dichtenden Eingriff mit dem Ventilsitz gezogen wird.A typical internal combustion engine uses an array of valves to control the intake and exhaust of gases into and out of an engine cylinder. The opening and closing of a valve is usually carried out electromagnetically or purely mechanically, by the valve stem is actuated by a lever assembly, which in turn is controlled by a driven by the crankshaft of the engine camshaft. It is connected to the generally downward movement of the lever assembly and the associated actuation of the valve stem end lifting the valve head of its valve seat. This movement is counteracted by the restoring force of a correspondingly arranged valve spring, which ensures that the valve head is pulled back into its sealing engagement with the valve seat at a suitable time of the engine cycle.
Um zu vermeiden, dass Toleranzen im Ventiltrieb und Temperaturänderungen beim Betrieb des Verbrennungsmotors zu einem harten Aufeinandertreffen von Ventiltrieb und Ventilschaft führen und außerdem das sichere Schließen des Ventils zu gewährleisten, ist es bekannt zwischen Ventiltrieb und Ventilschaft ein Ventilspiel vorbestimmter (Mindest-)Größe vorzusehen. Dieses nimmt jedoch während des Betriebs des Verbrennungsmotors verschleißbedingt in seiner Größe zu, was zu unerwünschten Änderungen in der für den Betrieb des Motors notwendigen exakten Ventilsteuerung und gegebenenfalls zu daraus resultierenden Folgeschäden führt.In order to avoid tolerances in the valvetrain and temperature changes during operation of the internal combustion engine to a hard clash of valvetrain and valve stem and also to ensure the safe closing of the valve, it is known between valve train and valve stem to provide a valve clearance of predetermined (minimum) size. However, this increases during operation of the internal combustion engine due to wear in terms of its size, which leads to undesirable changes in the necessary for the operation of the engine exact valve timing and possibly resulting consequential damage.
Aus diesem Grund muß das Ventilspiel nach entsprechender Betriebsdauer des Verbrennungsmotors auf eine vorbestimmte Größe ein-/nachgestellt werden, was im allgemeinen mit beträchtlichen Kosten und längeren Ausfallzeiten verbunden ist. Überdies setzt diese Wartungsarbeit ein entsprechendes Fachwissen und eine gewisse apparative Ausstattung voraus.For this reason, the valve clearance must be adjusted / readjusted to a predetermined size after a corresponding period of operation of the internal combustion engine, which is generally associated with considerable costs and longer downtimes. Moreover, this maintenance work requires a corresponding expertise and a certain equipment.
Einen Ausweg können selbsttätig wirkende Systeme zum automatischen Ein-/Nachstellen des Ventilspiels bieten, die bekannt sind. Weit verbreitet ist ein selbsttätiger hydraulischer Ventilspielausgleich (
Solche hydraulischen Systeme haben jedoch den Nachteil, dass sie auf eine Druckölversorgung aus dem Schmierölkreis angewiesen sind und in ihrer Reaktionszeit von dem Öldruckaufbau und von der Ölviskosität abhängig sind. Überdies sind sie kompliziert im Aufbau und relativ teuer in der Herstellung, so dass deren Verwendung in einfachen Verbrennungsmotoren unpassend ist.However, such hydraulic systems have the disadvantage that they rely on a pressurized oil supply from the lubricating oil circuit and are dependent in their reaction time on the oil pressure build-up and on the oil viscosity. Moreover, they are complicated in construction and relative expensive to manufacture, so that their use in simple internal combustion engines is inappropriate.
Außerdem sind mechanisch wirkende Ventilspielausgleichsvorrichtungen bekannt.In addition, mechanically acting valve clearance compensation devices are known.
Die
Auch in der
In der
Demgegenüber ist es wünschenswert, über eine einfach und kostengünstig herzustellende, rein mechanische, selbsttätig wirkende Vorrichtung zum Ein-/Nachstellen des Ventilspiels zu verfügen.In contrast, it is desirable to have a simple and inexpensive to manufacture, purely mechanical, self-acting device for adjusting / adjusting the valve clearance.
Diese Aufgabe wird durch einen Kipphebel gemäß Anspruch 1 der vorliegenden Erfindung gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind durch die abhängigen Ansprüche angegeben.This object is achieved by a rocker arm according to
Erfindungsgemäß ist das eingangs genannte Ventilspieleinstellelement dadurch gekennzeichnet, dass es einen im Kipphebel drehbar gelagerten Hohlzylinder mit um den Hohlzylinderumfang ausgebildeten ebenen Flächen ("Gleitstein") und eine den Gleitstein in einer vorbestimmten Drehrichtung drehenden Drehfeder umfasst. Benachbarte ebene Flächen sind durch deren Flächenkanten voneinander abgegrenzt.According to the invention, the above-mentioned Ventilspieleinstellelement is characterized in that it comprises a rotatably mounted in the rocker arm hollow cylinder formed around the hollow cylinder circumference flat surfaces ("sliding block") and a sliding the sliding block in a predetermined direction of rotation torsion spring. Adjacent flat surfaces are delimited from one another by their surface edges.
Die Drehfeder zur Drehung des Gleitsteins in eine vorbestimmte Drehrichtung hat eine weitaus geringere Federkraft als die das Ventil schließende Ventilfeder, so dass das Schließen des Ventils keine Beeinträchtigung durch eine dem entgegen gerichteten Kraftkomponente der Federkraft der Drehfeder erfährt.The torsion spring for rotation of the sliding block in a predetermined direction of rotation has a much lower spring force than the valve closing the valve spring, so that the closing of the valve undergoes no impairment by an opposing force component of the spring force of the torsion spring.
Erfindungsgemäß ist der Gleitstein so gestaltet, dass die um den Umfang des Hohlzylinders ausgebildeten ebenen Flächen jeweils parallel zur Hohlzylinderachse angeordnet sind. Dies impliziert, dass es für jede ebene Fläche ein Lot auf die Hohlzylinderachse gibt. Dieses Lot stimmt in seiner Richtung mit einer Radialenrichtung der kreisförmigen Querschnitte des Hohlzylinders überein. Erfindungsgemäß definiert das Lot durch eine ebene Fläche auf die Hohlzylinderachse den kürzesten Abstand der ebenen Fläche von der Hohlzylinderachse.According to the invention, the sliding block is designed so that the flat surfaces formed around the circumference of the hollow cylinder are each arranged parallel to the hollow cylinder axis. This implies that there is a perpendicular to the hollow cylinder axis for each flat surface. This solder coincides in its direction with a radial direction of the circular cross sections of the hollow cylinder. According to the invention, the solder defines the shortest distance of the flat surface from the hollow cylinder axis by a flat surface on the hollow cylinder axis.
Die ebenen Flächen weisen zur Hohlzylinderachse parallele (und damit auch zueinander parallele) Flächenkanten auf. In Bezug auf die durch die Drehfeder bewirkte Drehung des Gleitsteins in eine vorbestimmte Richtung sind die zur Hohlzylinderachse parallelen Flachenkanten einer jeden ebenen Flächen zu unterscheiden in eine voraus eilende vordere Flächenkante und eine dieser nach eilende hintere Flächenkante.The flat surfaces have parallel to the hollow cylinder axis (and thus also parallel to each other) surface edges. With respect to the rotation of the sliding block caused by the torsion spring in a predetermined direction, the flat edges parallel to the hollow cylinder axis of each flat surface are to be distinguished into a leading leading surface edge and a trailing surface edge leading thereto.
Für den Gleitstein ist charakteristisch, dass seine ebenen Flächen in der zur vorbestimmten Drehrichtung entgegengesetzten Richtung zunehmende kürzeste Abstände von der Zylinderachse sowie einen zunehmenden radialen Abstand der zugehörigen hinteren Flächenkanten von der Zylinderachse aufweisen.It is characteristic of the sliding block that its flat surfaces in the direction opposite to the predetermined direction of rotation have increasing shortest distances from the cylinder axis and an increasing radial distance of the associated rear surface edges from the cylinder axis.
Erfindungsgemäß ist weiterhin vorgesehen, dass die ebenen Flächen infolge der durch die Drehfeder bewirkten selbsttätigen Drehung des Gleitsteins jeweils in eine Drehstellung zur Betätigung des Ventilschaftes gelangen. In Schlußstellung des Ventils und der entsprechenden Stellung des Kipphebels ergibt sich bei jeder Drehstellung einer ebenen Fläche aus der Differenz zwischen dem senkrechten Abstand der Drehachse des Hohlzylinders vom Ventilschaftende und dem kürzesten Abstand der ebenen Fläche von der Zylinderachse ein erstes vorbestimmtes Ventilspiel. In der Drehstellung zur Betätigung des Ventilschaftes ist im Rahmen eines gegebenen Ventilspiels bei jeder ebenen Fläche das selbsttätige Weiterdrehen des Gleitsteins durch Anlage der zugehörigen hinteren Flächenkante der ebenen Fläche an das Ventilschaftende ausgeschlossen. Die Federkraft der Drehfeder führt bei Anlage einer hinteren Flächenkante gegen das Ventilschaftende somit zu keiner Drehung des Gleitsteins, sondern zu einem Vorspannen des Gleitsteins in Drehrichtung.According to the invention, it is further provided that, as a result of the automatic rotation of the sliding block caused by the torsion spring, the flat surfaces each reach a rotational position for actuating the valve stem. In the final position of the valve and the corresponding position of the rocker arm results at each rotational position of a flat surface of the difference between the vertical distance of the axis of rotation of the hollow cylinder from the valve stem end and the shortest distance of the flat surface of the cylinder axis, a first predetermined valve clearance. In the rotational position for actuating the valve stem, the automatic further rotation of the sliding block is prevented by abutment of the associated rear surface edge of the flat surface to the valve stem end in the context of a given valve clearance at each flat surface. The spring force of the torsion spring thus results in the application of a rear surface edge against the valve stem end to no rotation of the Sliding block, but to bias the sliding block in the direction of rotation.
In der Schlußstellung des Ventils und der entsprechenden Stellung des Kipphebels neigt sich die ebene Fläche in der Stellung zur Betätigung des Ventilschaftes aufgrund der durch die Drehfeder bewirkten Anlage der zugehörigen hinteren Flächenkante zum Ventilschaftende. Bei Betätigung des Ventilschaftes durch Kippen des Kipphebels wird diese Neigung der ebenen Flächen gegenüber den Ventilschaftenden aufgehoben und die ebene Fläche liegt dann dem Ventilschaftende vollflächig auf.In the final position of the valve and the corresponding position of the rocker arm, the flat surface tilts in the position for actuating the valve stem due to the caused by the torsion spring system of the associated rear surface edge to the valve stem end. Upon actuation of the valve stem by tilting the rocker arm, this inclination of the flat surfaces is lifted relative to the valve stem ends and the flat surface is then the valve stem end over the entire surface.
Das so eingestellte Ventilspiel neigt verschleißbedingt zur Vergrößerung, so dass bei ausreichender Vergrößerung des Ventilspiels die hintere Flächenkante der ebenen Fläche in der Drehstellung zur Betätigung des Ventilschaftes die Anlage gegen das Ventilschaftende verliert, wodurch die selbsttätige Drehung des Gleitsteins aufgrund der Federkraft der Drehfeder einsetzt. Die Drehung kann selbstverständlich nur einsetzen, wenn die ebene Fläche in der Stellung zur Betätigung des Ventilschaftes dem Ventilschaftende nicht voll aufliegt, d.h. erst wenn das entsprechend vergrößerte Ventilspiel in der Schlußstellung des Ventils und der entsprechenden Stellung des Kipphebels vorliegt.The thus adjusted valve lash tends to increase due to wear, so that with sufficient increase in the valve clearance, the rear surface edge of the flat surface in the rotational position for actuating the valve stem, the system against the valve stem end, whereby the automatic rotation of the sliding block due to the spring force of the torsion spring begins. Of course, the rotation can only be used if the flat surface in the position for actuating the valve stem does not fully lie against the end of the valve stem, i. only when the corresponding enlarged valve clearance in the final position of the valve and the corresponding position of the rocker arm is present.
Erfindungsgemäß ist die selbsttätige Drehung des Gleitsteins durch Anlage der zur ebenen Fläche in der Stellung zur Betätigung des Ventilschaftes gehörenden hinteren Flächenkante gehindert, solange das Ventilspiel ein zweites vorbestimmtes Ventilspiel, das der Differenz zwischen dem radialen Abstand der hinteren Flächenkante der ebenen Fläche von der Zylinderachse und dem kürzesten Abstand dieser ebenen Fläche von der Zylinderachse entspricht, nicht erreicht. Ein Verschleiß der hinteren Flächenkante, mit dem in der Praxis zu rechnen ist, verkürzt allerdings das Nachstellintervall.According to the invention, the automatic rotation of the sliding block is hindered by abutment of the rear surface edge associated with the flat surface in the position for actuating the valve stem, as long as the valve clearance is a second predetermined valve clearance, that is the difference between the radial distance of the rear surface edge of the flat surface from the cylinder axis and corresponds to the shortest distance of this flat surface from the cylinder axis, not reached. A wear of the rear surface edge, which is expected in practice, however, shortens the adjustment interval.
Da der senkrechte Abstand der Drehachse des Hohlzylinders vom Ventilschaftende bei einer bestimmten Stellung des Kipphebels in der Schlußstellung des Ventils im wesentlichen konstant ist, kann dadurch, dass jede ebene Fläche durch die selbsttätige Drehung des Gleitsteins in die Drehstellung zur Betätigung des Ventilschaftes gelangt, über den zunehmenden kürzesten Abstand der ebenen Flächen von der Zylinderachse ein erstes vorbestimmtes Ventilspiel ein-bzw. nachgestellt werden.Since the vertical distance of the axis of rotation of the hollow cylinder from the valve stem end at a certain position of the rocker arm in the final position of the valve is substantially constant, characterized in that each flat surface passes through the automatic rotation of the sliding block in the rotational position for actuating the valve stem, over Increasing shortest distance of the flat surfaces of the cylinder axis a first predetermined valve clearance on or. be readjusted.
In der Grundeinstellung des Gleitsteins wird dieser so eingestellt, dass die ebene Fläche mit dem geringsten kürzesten Abstand von der Hohlzylinderachse in eine Drehstellung zur Betätigung des Ventilschaftes gelangt. Dabei wird das erste vorbestimmte Ventilspiel eingestellt.In the basic setting of the sliding block this is adjusted so that the flat surface with the smallest shortest distance from the hollow cylinder axis reaches a rotational position for actuating the valve stem. In this case, the first predetermined valve clearance is set.
Vorzugsweise ist die Kipphebel so gestaltet, dass die Drehfeder eine um die Hohlzylinderachse angeordnete, zweigelagerte Schraubenfeder ist, die ein Festlager am Gleitstein und das andere Festlager am Kipphebel hat. Dies vereinfacht die Konstruktion, spart Raum und Kosten.Preferably, the rocker arm is designed so that the torsion spring is arranged around the hollow cylinder axis, two-bearing coil spring, which has a fixed bearing on the sliding block and the other fixed bearing on the rocker arm. This simplifies the design, saves space and costs.
Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, dass der Kipphebel mit wenigstens vier ebenen Flächen ausgestattet ist, wodurch wenigstens ein viermaliges Ein-/Nachstellen des ersten vorbestimmten Ventilspiels erfasst werden kann.An advantageous embodiment of the invention provides that the rocker arm is equipped with at least four flat surfaces, whereby at least a four times Adjustment / readjustment of the first predetermined valve clearance can be detected.
Weiterhin ist es bevorzugt, dass das erste vorbestimmte Ventilspiel für jede ebene Fläche in ihrer Drehstellung zur Betätigung des Ventilschaftes gleich ist. Hierdurch wird ein mehrmaliges Nachstellen des Ventilspiels auf einen jeweils gleichen vorgegebenen Wert erreicht. Insbesondere kann beispielsweise für jede Nachstellstufe ein konstantes Mindestventilspiel eingestellt werden.Furthermore, it is preferred that the first predetermined valve clearance for each flat surface is the same in its rotational position for actuating the valve stem. As a result, a multiple readjustment of the valve clearance is achieved to a respective same predetermined value. In particular, for example, a constant minimum valve clearance can be set for each readjustment stage.
Desgleichen ist es bevorzugt, dass das zweite vorbestimmte Ventilspiel für jede ebene Fläche in ihrer Drehstellung zur Betätigung des Ventilschaftes gleich ist. Hierdurch ist sichergestellt, dass ein bestimmtes, jeweils für jede ebene Fläche in der Drehstellung zur Betätigung des Ventilschaftes gleiches Ventilspiel nicht überschritten wird. In Verbindung mit einem konstanten ersten vorbestimmten Ventilspiel kann so das Ventilspiel innerhalb der durch das erste und das zweite vorbestimmte Ventilspiel definierten Grenzen gehalten werden.Likewise, it is preferred that the second predetermined valve clearance be the same for each flat surface in its rotational position for actuating the valve stem. This ensures that a certain, for each flat surface in the rotational position for actuating the valve stem equal valve clearance is not exceeded. In conjunction with a constant first predetermined valve clearance, the valve clearance can thus be kept within the limits defined by the first and the second predetermined valve clearance.
In bevorzugter Weise liegt das erste vorbestimmte Ventilspiel im Bereich von 0,01 mm - 1 mm; dieses beträgt vorzugsweise 0,1 mm.Preferably, the first predetermined valve clearance is in the range of 0.01 mm - 1 mm; this is preferably 0.1 mm.
In bevorzugter Weise weist das zweite vorbestimmte Ventilspiel eine Differenz zum ersten vorbestimmten Ventilspiel auf, die im Bereich von 0,05 mm - 1 mm liegt; diese beträgt vorzugsweise 0,2 mm.Preferably, the second predetermined valve clearance has a difference to the first predetermined valve clearance, which is in the range of 0.05 mm - 1 mm; this is preferably 0.2 mm.
Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, dass die ebenen Flächen des Gleitsteins beiderseitig von auf den Hohlzylinder aufgezogenen Beilagscheiben begrenzt werden. Hierdurch kann der Gleitstein in seiner drehbaren Lagerung im Kipphebel bezüglich seiner Auslenkung in Richtung der Drehachse einfach und zugleich wirksam fixiert werden, ohne dabei die selbsttätige Drehung des Gleitsteins zu beeinträchtigen.An advantageous embodiment of the invention provides that the flat surfaces of the sliding block on both sides be limited by mounted on the hollow cylinder washers. In this way, the sliding block in its rotatable mounting in the rocker arm with respect to its deflection in the direction of the axis of rotation can be easily and simultaneously effectively fixed without affecting the automatic rotation of the sliding block.
Erfindungsgemäß ist es ferner bevorzugt, dass das zweite vorbestimmte Ventilspiel der ebenen Fläche mit dem größten kürzesten Abstand, d.h. diejenige ebene Fläche, die als letzte in die Drehstellung zur Betätigung des Ventilschaftes einrastet, so groß gewählt ist, dass für eine durchschnittliche Betriebsdauer des Verbrennungsmotors die Anlage der hinteren Flächenkante gewährleistet ist. Dadurch wird die ebene Fläche mit dem größten kürzesten Abstand von der Hohlzylinderachse, d.h. mit der maximalen Fähigkeit zum Ausgleich der verschleißbedingten Abnutzung, permanent für die restliche Betriebsdauer des Verbrennungsmotors benutzt.According to the invention it is further preferred that the second predetermined valve clearance of the flat surface with the greatest shortest distance, i. that plane surface which engages as the last in the rotational position for actuating the valve stem, is chosen so large that the system of the rear surface edge is ensured for an average operating time of the internal combustion engine. Thereby, the flat surface with the largest shortest distance from the hollow cylinder axis, i. with the maximum ability to compensate for wear-related wear, used permanently for the remainder of the operating life of the engine.
Vorzugsweise ist der Gleitstein aus Hartguss, Sinterwerkstoff, kaltgepreßtem oder im Strangpreßverfahren geformten Stahl gefertigt.Preferably, the sliding block is made of chilled cast iron, sintered material, cold-formed or extruded steel.
Wie bereits dargelegt kann die vorliegende erfindungsgemäße Vorrichtung einfach und kostengünstig hergestellt werden. Ein besonderer Vorteil der Erfindung liegt jedoch darin, dass sie sehr wenig Raum beansprucht und praktisch universell einsetzbar ist. Zudem lassen sich auch bereits gefertigte Verbrennungsmotoren, die einen Kipphebel verwenden, einfach und preiswert umrüsten, indem der bisher verwendete Kipphebel mit dem erfindungsgemäßen Kipphebel ausgetauscht wird.As already stated, the present device according to the invention can be produced simply and inexpensively. However, a particular advantage of the invention lies in the fact that it requires very little space and is practically universally applicable. In addition, already manufactured internal combustion engines that use a rocker arm, easily and inexpensively retool by replacing the previously used rocker arm with the rocker arm according to the invention.
Im folgenden wird die Erfindung beispielhaft unter Bezugnahme auf die beigefügten Zeichnungen dargestellt.
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Fig. 1 zeigt in perspektivischer Ansicht einen erfindungsgemäßen Kipphebel in Eingriff mit einem Ventilschaft; -
Fig. 2a zeigt in Draufsicht einen Teil des erfindungsgemäßen Kipphebels; -
Fig. 2b zeigt in Draufsicht einen vergrößerten Ausschnitt des erfindungsgemäßen Kipphebels derFig. 2a ; -
Fig. 3 zeigt eine Querschnittsansicht eines ersten Beispiels des Gleitsteins mit sieben ebenen Flächen; und -
Fig. 4 zeigt eine Querschnittsansicht eines zweiten Beispiels des Gleitsteins mit neun ebenen Flächen.
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Fig. 1 shows in perspective view a rocker arm according to the invention in engagement with a valve stem; -
Fig. 2a shows in plan view a part of the rocker arm according to the invention; -
Fig. 2b shows in plan view an enlarged detail of the rocker arm of the inventionFig. 2a ; -
Fig. 3 shows a cross-sectional view of a first example of the sliding block with seven flat surfaces; and -
Fig. 4 shows a cross-sectional view of a second example of the sliding block with nine flat surfaces.
Wie aus
In der Grundeinstellung des Gleitsteins 2 steht die ebene Fläche des Gleitsteins mit dem geringsten kürzesten Abstand, d. h. dem kürzesten Lot der jeweiligen ebenen Fläche auf die Hohlzylinderachse, in Eingriff mit dem Ventilschaftende. Zwischen jeder ebenen Fläche in der Drehstellung zur Betätigung des Ventilschaftendes und dem Ventilschaft liegt in der Schlußstellung des Ventils und der entsprechende Stellung des Kipphebels 1 das Ventilspiel vor. Durch die über die Federkraft der Drehfeder 5 bewirkten selbsttätigen Drehung des Gleitsteins 2 neigt sich die in Betätigungsstellung befindliche ebene Fläche zum Ventilschaftende.In the basic setting of the sliding
Bei Kippen des Kipphebels 1 zur Öffnung des Ventils bewegt sich dessen mit dem Gleitstein 2 ausgestattetes Ende im Uhrzeigersinn nach unten und betätigt gleichzeitig das mit dem Gleitstein 2 in Eingriff stehende Ventilschaftende. Bei dieser Bewegung muß der Kipphebel 1 zunächst die Wegstrecke des Ventilspiels zurück legen, bevor die ebene Fläche dem Ventilschaftende voll aufliegt.When tilting the
Soll das Ventil zu einem geeigneten Zeitpunkt des Motorzyklus wieder geschlossen, d.h. der Ventilteller wieder zurück in seinen dichtenden Eingriff mit dem Ventilring im Zylinderkopf gezogen werden, kippt der Kipphebel 2 entgegen dem Uhrzeigersinn wieder in seine Ausgangsposition zurück und der Ventilschaft 4 folgt dieser Bewegung aufgrund der Federkraft der Ventilfeder 8, ohne dabei den Eingriff mit der ebenen Fläche des Gleitsteins 2 zu verlieren.If the valve is closed again at a suitable time of the engine cycle, ie, the valve disk is pulled back into its sealing engagement with the valve ring in the cylinder head, the
In der Endstellung des Kipphebels 1 hat dessen mit dem Gleitstein 2 ausgerüstetes Ende wieder einen Abstand vom Ventilschaftende, bei dem das Ventilspiel zwischen der in Eingriff mit dem Ventilschaftende stehenden ebenen Fläche und dem Ventilschaftende ermöglicht ist.In the end position of the
Die ebene Fläche bleibt in Eingriff mit dem Ventilschaftende, solange die in Drehrichtung des Gleitsteins 2 nach eilende hintere Flächenkante gegen das Ventilschaftende anliegt. Der Gleitstein 2 wird durch die Drehfeder 5 in diesem Zustand lediglich vorgespannt.The flat surface remains in engagement with the valve stem end, as long as in the direction of rotation of the sliding
Vergrößert sich das Ventilspiel im Laufe der Betriebsdauer des Motors kann das Ventilspiel so groß werden, dass es den Wert des zweiten vorbestimmten Ventilspiels erreicht, bei dem die hintere Flächenkante nicht mehr gegen das Ventilschaftende anliegt. Der Gleitstein wird dann aufgrund der vorspannenden Federkraft der Drehfeder gedreht, bis die nächste ebene Fläche durch Anlage ihrer hinteren Flächenkante in die Drehstellung zur Betätigung des Ventilschaftes gelangt. Das ursprünglich vergrößerte Ventilspiel wird dabei durch den vergleichsweise größeren kürzesten Abstand der ebenen Fläche wieder verringert und auf das erste vorbestimmte Ventilspiel eingestellt.As the valve clearance increases over the life of the engine, the valve clearance may become so great as to reach the value of the second predetermined valve clearance where the rear surface edge is no longer against the valve stem end. The sliding block is then rotated due to the biasing spring force of the torsion spring until the next flat surface passes through their rear surface edge resting in the rotational position for actuating the valve stem. The originally enlarged valve clearance is reduced again by the comparatively larger shortest distance of the flat surface and adjusted to the first predetermined valve clearance.
Sobald in der ersten Stufe das Ventilspiel beispielsweise den Wert 0,3 mm erreicht, dreht sich der Gleitstein auf die nächste Flächenstufe und man erhält sofort wieder das Ausgangsventilspiel von beispielsweise 0,1 mm. Es wird also sichergestellt, dass immer ein Mindestventilspiel vorliegt und die Ventile nicht offen bleiben.As soon as in the first stage, the valve clearance, for example, reaches the value 0.3 mm, the sliding block rotates to the next surface level and you immediately get back to the output valve clearance, for example, 0.1 mm. It is thus ensured that always a minimum valve clearance is present and the valves do not remain open.
Die
In
Das erste vorbestimmte Ventilspiel ergibt sich aus der Differenz zwischen dem senkrechten Abstand der Drehachse des Hohlzylinders vom Ventilschaftende und dem kürzesten Abstand der ebenen Fläche von der Zylinderachse. In der Grundeinstellung des Gleitsteins liegt das erste vorbestimmte Ventilspiel also innerhalb der Differenz zwischen R1 und R1+x1.The first predetermined valve clearance results from the difference between the vertical distance of the axis of rotation of the hollow cylinder from the valve stem end and the shortest distance of the flat surface from the cylinder axis. In the basic setting of the sliding block, the first predetermined valve clearance thus lies within the difference between R 1 and R 1 + x 1 .
Das zweite vorbestimmte Ventilspiel entspricht der Differenz zwischen dem radialen Abstand der hinteren Flächenkante der ebenen Fläche von der Zylinderachse und dem kürzesten Abstand der ebenen Fläche von der Zylinderachse. In der Grundeinstellung des Gleitsteins beträgt das zweite vorbestimmte Ventilspiel also x1.The second predetermined valve clearance corresponds to the difference between the radial distance of the rear surface edge of the flat surface from the cylinder axis and the shortest distance of the flat surface from the cylinder axis. In the basic setting of the sliding block, the second predetermined valve clearance is thus x 1 .
Solange das Ventilspiel die volle Differenz zwischen R1 und R1+x1, d.h. x1, nicht erreicht, ist die selbsttätige Drehung des Gleitsteins durch die Anlage der hinteren Flächenkante an das Ventilschaftende gehindert.As long as the valve clearance does not reach the full difference between R 1 and R 1 + x 1 , ie x 1 , the automatic rotation of the sliding block is hindered by the abutment of the rear surface edge against the valve stem end.
Sobald das Ventilspiel den Wert von x1 erreicht, springt der Gleitstein in die nächste Rastlage über, bei der die in der zur Drehrichtung gegensätzlichen Richtung nächste ebene Fläche in Eingriff mit dem Ventilschaftende gelangt. Der kürzeste Abstand der ebenen Fläche von der Drehachse beträgt nunmehr R2=R1+x1-y1. In dieser Stellung des Gleitsteins liegt das erste vorbestimmte Ventilspiel innerhalb der Differenz zwischen R2=R1+x1-y1 und R2+x2. Das zweite vorbestimmte Ventilspiel beträgt x2.As soon as the valve clearance reaches the value of x 1 , the sliding block jumps over to the next detent position, at which point the next flat surface in the direction opposite to the direction of rotation comes into engagement with the valve stem end. The shortest distance of the flat surface from the axis of rotation is now R 2 = R 1 + x 1 -y 1 . In this position of the sliding block, the first predetermined valve clearance is within the difference between R 2 = R 1 + x 1 -y 1 and R 2 + x 2 . The second predetermined valve clearance is x 2 .
Solange das Ventilspiel die volle Differenz zwischen R2=R1+x1-y1 und R2+x2, d.h. x2, nicht erreicht, ist die selbsttätige Drehung des Gleitsteins durch die Anlage der hinteren Flächenkante an das Ventilschaftende gehindert.As long as the valve clearance does not reach the full difference between R 2 = R 1 + x 1 -y 1 and R 2 + x 2 , ie x 2 , the automatic rotation of the sliding block is hindered by the abutment of the rear surface edge against the valve stem end.
Sobald das Ventilspiel den Wert von x2 erreicht, springt der Gleitstein in die nächste Rastlage über, bei der wiederum die in der zur Drehrichtung gegensätzlichen Richtung nächste ebene Fläche in Eingriff mit dem Ventilschaftende gelangt. Der kürzeste Abstand der ebenen Fläche von der Drehachse beträgt nunmehr R3=R2+x2-y2.As soon as the valve clearance reaches the value of x 2 , the sliding block jumps over to the next locking position, at which in turn the next flat surface in the direction opposite to the direction of rotation comes into engagement with the valve stem end. The shortest distance of the flat surface from the axis of rotation is now R 3 = R 2 + x 2 -y 2 .
In dieser Stellung des Gleitsteins liegt das erste vorbestimmte Ventilspiel innerhalb der Differenz zwischen R3=R2+x2-y2 und R3+x3. Das zweite vorbestimmte Ventilspiel beträgt x3. Solange das Ventilspiel die volle Differenz zwischen R3=R2+x2-y2 und R3+x3, d.h. x3, nicht erreicht ist die selbsttätige Drehung des Gleitsteins durch die Anlage der hinteren Flächenkante an das Ventilschaftende gehindert.In this position of the sliding block, the first predetermined valve clearance is within the difference between R 3 = R 2 + x 2 -y 2 and R 3 + x 3 . The second predetermined valve clearance is x 3 . As long as the valve clearance does not reach the full difference between R 3 = R 2 + x 2 -y 2 and R 3 + x 3 , ie x 3 , the automatic rotation of the sliding block is hindered by the abutment of the rear surface edge against the valve stem end.
Sobald das Ventilspiel den Wert von x3 erreicht, springt der Gleitstein in die nächste Rastlage über, bei der dann die in der zur Drehrichtung gegensätzlichen Richtung nächste ebene Fläche in Eingriff mit dem Ventilschaftende gelangt. Für alle weiteren ebenen Flächen gilt eine analoge Betrachtung. Die Anzahl der Stufen kann je nach Bedarf gewählt werden. Beispielsweise ist ein Verschleiß von 1 mm problemlos zu kompensieren. In
Die ersten und zweiten vorbestimmten Ventilspiele sind für jede ebene Fläche gleich. Das erste vorbestimmte Ventilspiel beträgt 0,1 mm. Jedesmal wenn die nächste ebene Fläche die Drehstellung zur Betätigung des Ventilschaftes einnimmt, wird das erste vorbestimmte Ventilspiel von 0,1 mm nachgestellt. In der Grundeinstellung wird ein Ventilspiel von 0,1 mm eingestellt. Das zweite vorbestimmte Ventilspiel beträgt 0,3 mm. Die Differenz zwischen dem zweiten vorbestimmten Ventilspiel und dem ersten vorbestimmten Ventilspiel beträgt 0,2 mm. Jede ebene Fläche rastet nach einem Verschleiß von 0,2 mm in die Drehstellung zur Betätigung des Ventilschaftes und verringert das tatsächliche Ventilspiel von 0,3 mm wieder auf 0,1 mm. Zusätzlich sind die Winkel zwischen den benachbarten Loten durch die ebenen Flächen auf die Hohlzylinderachse angegeben.
The first and second predetermined valve clearances are the same for each flat surface. The first predetermined valve clearance is 0.1 mm. Each time the next flat surface assumes the rotational position for actuating the valve stem, the first predetermined valve clearance of 0.1 mm is readjusted. In the default setting, a valve clearance of 0.1 mm is set. The second predetermined valve clearance is 0.3 mm. The difference between the second predetermined valve clearance and the first predetermined valve clearance is 0.2 mm. Each flat surface snaps into the rotational position to actuate the valve stem after 0.2 mm of wear and reduces the actual valve clearance from 0.3 mm back to 0.1 mm. In addition, the angles between the adjacent solders are indicated by the flat surfaces on the hollow cylinder axis.
In diesem Beispiel hat der Hohlzylinder eine Länge von 14,4 mm, einen äußeren Durchmesser von 7 mm und einen inneren Durchmesser von 3,7 mm. Die ebenen Flächen haben eine Breite entlang der Hohlzylinderachse von 6 mm. Die Länge des Hohlzylinders beiderseits des mit ebenen Flächen besetzten Bereichs beträgt jeweils 4,2 mm.In this example, the hollow cylinder has a length of 14.4 mm, an outer diameter of 7 mm and an inner diameter of 3.7 mm. The flat surfaces have a width along the hollow cylinder axis of 6 mm. The length of the hollow cylinder on both sides of the area occupied by flat surfaces is 4.2 mm in each case.
Mit dem erfindungsgemäßen Kipphebel, ausgestattet mit der Vorrichtung zum Ein-/Nachstellen des Ventilspiels gemäß den vorliegenden Beispielen kann eine durchschnittliche Standzeit von 5000 Stunden erreicht werden, bis die letzte eben Fläche in die Drehstellung zum Betätigen des Ventilschaftes einrastet. Die hintere Flächenkante der letzten ebenen Fläche ist dabei so ausgelegt, dass während der noch folgenden durchschnittlichen Betriebsdauer des Verbrennungsmotors die Betätigung des Ventilschaftes nur noch durch die letzte ebene Fläche erfolgt.With the rocker arm according to the invention, equipped with the device for adjusting / adjusting the valve clearance according to the present examples, an average service life of 5000 hours can be achieved until the last flat surface engages in the rotational position for actuating the valve stem. The back Surface edge of the last flat surface is designed so that during the still following average operating time of the internal combustion engine, the actuation of the valve stem takes place only through the last flat surface.
In den gezeigten Beispielen wurden sieben bzw. neun ebene Flächen zur Ein-/Nachstellung des Ventilspiels gezeigt. Theoretisch sind noch wesentlich mehr kürzere ebene Flächen mit kürzeren Nachstellintervallen denkbar, bis hin zur angenäherten Spirale aus ebenen Flächen; letztere setzt voraus, dass die Reibung ein Durchrutschen verhindert. Dann läge ständig eine Linienanlagerung vor, ähnlich der Anlage bei den Aufstandsflächen. Hier bewirkt eine Abnutzung der Hinterkante ebenfalls eine Verkürzung des Nachstellintervalls. In the examples shown, seven or nine flat surfaces for adjusting / re-adjusting the valve clearance were shown. Theoretically, even more shorter flat surfaces with shorter readjustment intervals are conceivable, up to the approximate spiral of flat surfaces; the latter assumes that the friction prevents slipping. Then there would always be a line appendage, similar to the plant at the footprints. Here wear of the trailing edge also causes a shortening of the Nachstellintervalls.
Claims (10)
- A rocker arm for a valve train of an internal combustion engine for the opening actuation of a valve stem (4) against the spring force of a valve spring (8) closing the valve, provided with a mechanical valve play adjusting element, characterized in that said valve play adjusting element comprises a slide ring (2) rotationally mounted in said rocker arm (1) formed as a hollow cylinder with planar surfaces around the hollow cylindrical circumference and a torsion spring (5) rotating said slide ring (2) in a predetermined rotational direction, whereina) said planar surfaces are arranged, respectively, parallel to the hollow cylinder axis and the perpendicular on the respective planar surface by the hollow cylinder axis corresponds to the shortest distance of the planar surface of the hollow cylinder axis,b) said planar surfaces comprise, respectively, a front surface edge preceding in the predetermined rotational direction and a rear surface edge following closely behind thereto, which are parallel to said hollow cylinder axis,c) said planar surfaces in the opposite direction to the predetermined rotational direction show, respectively, increasing shortest distances from the cylinder axis and an increasing radial distance of the associated rear surface edge from the cylinder axis,d) said planar surfaces due to the automatic rotation of said slide ring (2), respectively, reach the next rotational position for actuating the valve stem by which a first predetermined valve play results from the difference between the perpendicular distance of the rotational axis of the hollow cylinder from said valve shaft end and the shortest distance of the planar surface from the cylinder axis, wherein the automatic rotation of the slide ring (2) is prevented through the contact of the rear surface edge of the planar surface at the valve stem end as long as a second predetermined valve play is not reached which is greater than the first predetermined valve play and corresponds to the difference between the radial distance of the rear surface edge of the planar surface from the cylinder axis and the shortest distance of the planar surface from the cylinder axis.
- The rocker arm according to claim 1,
characterized in that
said torsion spring (5) is a dual-supported helical spring arranged around said hollow cylinder axis, having a fixed bearing on said slide ring (2) and the other fixed bearing at the slide ring (2). - The rocker arm according to claims 1 and 2,
characterized in that
said slide ring (2) comprises at least four planar surfaces. - The rocker arm according to one of the claims 1 to 3,
characterized in that
said first predetermined valve play is the same for each planar surface in its rotational position for actuating said valve stem (4). - The rocker arm according to one of the claims 1 to 4,
characterized in that
said second predetermined valve play is the same for each planar surface in its rotational position for actuating said valve stem (4). - The rocker arm according to the claims 1 to 5,
characterized in that
said first predetermined valve play lies in the region of 0.01 mm - 1 mm, preferably, however, amounts to 0.1 mm. - The rocker arm according to one of the claims 1 to 6,
characterized in that
said second predetermined valve play shows a difference to said first predetermined valve play, which lies within the range of 0.01 mm - 1 mm, preferably amounts, however, to 0.2 mm. - The rocker arm according to one of the claims 1 to 7,
characterized in that
said planar surfaces of said slide ring (2) are mutually defined by shims drawn up on said hollow cylinder. - The rocker arm according to one of the claims 1 to 8,
characterized in that
said second predetermined valve play of the planar surface with the largest shortest distance is selected so large that for an average operating life of the internal combustion motor the contact of the rear surface edge is ensured. - The rocker arm according to one of the claims 1 to 9,
characterized in that
said slide ring (2) is made from chilled casting, sintered material, cold-pressed steel or steel formed in the extrusion moulding method
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10105807A DE10105807C1 (en) | 2001-02-08 | 2001-02-08 | Pivot lever for operation of internal combustion engine valve has mechanical valve play setting element using rotatable hollow cylinder with planar surfaces for operation of valve shaft |
DE10105807 | 2001-08-02 | ||
PCT/EP2002/000251 WO2002063142A1 (en) | 2001-02-08 | 2002-01-12 | Rocker arm for a valve train in an internal combustion engine with device for independent setting/adjustment of the valve play |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1358397A1 EP1358397A1 (en) | 2003-11-05 |
EP1358397B1 true EP1358397B1 (en) | 2008-07-02 |
Family
ID=7673337
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02715421A Expired - Lifetime EP1358397B1 (en) | 2001-02-08 | 2002-01-12 | Rocker arm for a valve train in an internal combustion engine with device for independent setting/adjustment of the valve play |
Country Status (5)
Country | Link |
---|---|
US (1) | US6612278B2 (en) |
EP (1) | EP1358397B1 (en) |
CN (1) | CN1255620C (en) |
DE (2) | DE10105807C1 (en) |
WO (1) | WO2002063142A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7883539B2 (en) | 1997-01-02 | 2011-02-08 | Edwards Lifesciences Llc | Heart wall tension reduction apparatus and method |
US6332893B1 (en) | 1997-12-17 | 2001-12-25 | Myocor, Inc. | Valve to myocardium tension members device and method |
US6260552B1 (en) | 1998-07-29 | 2001-07-17 | Myocor, Inc. | Transventricular implant tools and devices |
US6723038B1 (en) | 2000-10-06 | 2004-04-20 | Myocor, Inc. | Methods and devices for improving mitral valve function |
US6764510B2 (en) | 2002-01-09 | 2004-07-20 | Myocor, Inc. | Devices and methods for heart valve treatment |
DE10237560B4 (en) * | 2002-08-16 | 2007-11-08 | Man Nutzfahrzeuge Ag | Backlash-free valve train for an internal combustion engine |
US7112219B2 (en) | 2002-11-12 | 2006-09-26 | Myocor, Inc. | Devices and methods for heart valve treatment |
DE102012001633A1 (en) * | 2012-01-30 | 2013-08-01 | Kolbenschmidt Pierburg Innovations Gmbh | Mechanically controllable valve train arrangement |
CN107676141A (en) * | 2017-11-15 | 2018-02-09 | 宁波里尔汽车技术有限公司 | Mechanical valve clearance adjustment mechanism |
CN115247582B (en) * | 2021-04-26 | 2023-07-21 | 北京福田康明斯发动机有限公司 | Method and device for adjusting engine valve clearance |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1948063A (en) * | 1932-08-17 | 1934-02-20 | Thompson Prod Inc | Mechanical clearance regulator |
DE621553C (en) * | 1933-09-07 | 1935-11-12 | Gen Motors Res Corp | Device to compensate for the game in the valve drive of internal combustion engines u. like |
US2365401A (en) * | 1943-09-17 | 1944-12-19 | Fisk John Edwin | Tappet |
US2791260A (en) * | 1954-04-21 | 1957-05-07 | William I Pixley | Guide means for roll straighteners |
FR1207052A (en) * | 1957-06-26 | 1960-02-15 | Ford | Valve control mechanism |
FR1207502A (en) | 1958-06-13 | 1960-02-17 | Herman Pneumatic Machine Co | Improvements to processes and devices for packing foundry molds |
US3658038A (en) * | 1971-01-04 | 1972-04-25 | Johnson Products Inc | Tappet for overhead camshaft engine |
JP2508062B2 (en) * | 1987-03-19 | 1996-06-19 | 三菱自動車工業株式会社 | Locker arm using roller bearing |
EP0331901B1 (en) * | 1988-02-05 | 1993-11-18 | Dieter Voigt | Valve drive for a lift valve |
DE3901966A1 (en) * | 1988-02-05 | 1989-08-17 | Volkswagen Ag | Valve drive for a reciprocating valve with mechanical compensation of the valve play |
DE4339433A1 (en) * | 1993-11-18 | 1995-05-24 | Bayerische Motoren Werke Ag | Drag lever for valve in vehicle combustion engine |
-
2001
- 2001-02-08 DE DE10105807A patent/DE10105807C1/en not_active Expired - Fee Related
-
2002
- 2002-01-12 EP EP02715421A patent/EP1358397B1/en not_active Expired - Lifetime
- 2002-01-12 CN CN02800249.0A patent/CN1255620C/en not_active Expired - Fee Related
- 2002-01-12 DE DE50212436T patent/DE50212436D1/en not_active Expired - Lifetime
- 2002-01-12 WO PCT/EP2002/000251 patent/WO2002063142A1/en active IP Right Grant
- 2002-10-07 US US10/267,106 patent/US6612278B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP1358397A1 (en) | 2003-11-05 |
CN1457386A (en) | 2003-11-19 |
DE50212436D1 (en) | 2008-08-14 |
US6612278B2 (en) | 2003-09-02 |
WO2002063142A1 (en) | 2002-08-15 |
CN1255620C (en) | 2006-05-10 |
US20030029404A1 (en) | 2003-02-13 |
DE10105807C1 (en) | 2002-05-08 |
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