EP1358397B1 - Culbuteur pour mecanisme de distribution de moteur a combustion interne et dispositif d'ajustement/reajustement automatique du jeu des soupapes - Google Patents

Culbuteur pour mecanisme de distribution de moteur a combustion interne et dispositif d'ajustement/reajustement automatique du jeu des soupapes Download PDF

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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
Application number
EP02715421A
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German (de)
English (en)
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EP1358397A1 (fr
Inventor
Günter Kampichler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Motorenfabrik Hatz GmbH and Co KG
Original Assignee
Motorenfabrik Hatz GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Motorenfabrik Hatz GmbH and Co KG filed Critical Motorenfabrik Hatz GmbH and Co KG
Publication of EP1358397A1 publication Critical patent/EP1358397A1/fr
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Publication of EP1358397B1 publication Critical patent/EP1358397B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • 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
    • 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)

Claims (10)

  1. Culbuteur pour un mécanisme de distribution d'un moteur à combustion interne pour l'actionnement d'ouverture d'une tige de soupape (4) contrairement à la force de ressort d'un ressort de soupape (8) fermant la soupape, équipé d'un élément de réglage mécanique de jeu de soupape,
    caractérisé en ce que
    l'élément de réglage du jeu de soupape comporte un coulisseau (2) monté de façon pivotante dans le culbuteur (1) sous forme de cylindre creux avec des surfaces planes réalisées autour du pourtour du cylindre creux et un ressort de rotation (5) faisant tourner le coulisseau (2) dans un sens de rotation prédéfini,
    a) les surfaces planes étant disposées respectivement parallèlement à l'axe du cylindre creux et la perpendiculaire à la surface plane respective et passant par l'axe du cylindre creux correspondant à la distance la plus courte de la surface plane à l'axe du cylindre creux,
    b) les surfaces planes présentant chacune une arête de surface avant précédant dans le sens de rotation prédéfini et une arête de surface arrière suivant cette arête, lesquelles sont parallèles à l'axe du cylindre creux,
    c) les surfaces planes présentant dans la direction opposée au sens de rotation prédéfini à chaque fois des distances très courtes croissantes à l'axe du cylindre et une distance radiale croissante des arêtes de surface arrière spécifiques à l'axe du cylindre,
    d) les surfaces planes arrivant du fait de la rotation automatique du coulisseau (2) respectivement dans le prochain sens de rotation pour l'actionnement de la tige de soupape, avec lequel un premier jeu de soupape prédéfini est obtenu à partir de la différence entre la distance verticale de l'axe de rotation du cylindre creux à l'extrémité de la tige de soupape et la distance la plus courte de la surface plane à l'axe du cylindre, la rotation automatique du coulisseau (2) étant gênée par l'appui de l'arête de surface arrière de la surface plane sur l'extrémité de la tige de soupape aussi longtemps qu'un second jeu de soupape prédéfini, qui est supérieur au premier jeu de soupape prédéfini et correspond à la différence entre la distance radiale de l'arête de surface arrière de la surface plane à l'axe du cylindre et la distance la plus courte de la surface plane à l'axe du cylindre, n'est pas atteint.
  2. Culbuteur selon la revendication 1,
    caractérisé en ce que
    le ressort de rotation (5) est un ressort hélicoïdal monté par deux et disposé autour de l'axe de cylindre creux, lequel ressort présente un palier fixe sur le coulisseau (2) et l'autre palier fixe sur le culbuteur.
  3. Culbuteur selon les revendications 1 et 2,
    caractérisé en ce que
    le coulisseau (2) présente au moins quatre surfaces planes.
  4. Culbuteur selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    le premier jeu de soupape prédéfini est identique pour chaque surface plane dans son sens de rotation pour l'actionnement de la tige de soupape (4).
  5. Culbuteur selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    le second jeu de soupape prédéfini est identique pour chaque surface plane dans son sens de rotation pour l'actionnement de la tige de soupape (4).
  6. Culbuteur selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce que
    le premier jeu de soupape prédéfini est de l'ordre de 0,01 mm à 1 mm, mais de préférence de 0,1 mm.
  7. Culbuteur selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que
    le second jeu de soupape prédéfini présente une différence par rapport au premier jeu de soupape prédéfini qui est de l'ordre de 0,01 mm à 1 mm, mais de préférence de 0,2 mm.
  8. Culbuteur selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    les surfaces planes du coulisseau (2) sont limitées des deux côtés par des rondelles montées sur le cylindre creux.
  9. Culbuteur selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    le second jeu de soupape prédéfini de la surface plane avec la distance maximale la plus courte est choisie suffisamment grand pour que l'appui de l'arête de surface arrière soit garanti pour une durée de service moyenne du moteur à combustion.
  10. Culbuteur selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que
    le coulisseau (2) est fabriqué à base de fonte dure, de matériau fritté, d'acier comprimé à froid ou formé dans le procédé d'extrusion.
EP02715421A 2001-02-08 2002-01-12 Culbuteur pour mecanisme de distribution de moteur a combustion interne et dispositif d'ajustement/reajustement automatique du jeu des soupapes Expired - Lifetime EP1358397B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10105807A DE10105807C1 (de) 2001-02-08 2001-02-08 Kipphebel für einen Ventiltrieb eines Verbrennungsmotors mit Vorrichtung zur selbsttätigen Ein-/Nachstellung des Ventilspiels
DE10105807 2001-08-02
PCT/EP2002/000251 WO2002063142A1 (fr) 2001-02-08 2002-01-12 Culbuteur pour mecanisme de distribution de moteur a combustion interne et dispositif d'ajustement/reajustement automatique du jeu des soupapes

Publications (2)

Publication Number Publication Date
EP1358397A1 EP1358397A1 (fr) 2003-11-05
EP1358397B1 true EP1358397B1 (fr) 2008-07-02

Family

ID=7673337

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02715421A Expired - Lifetime EP1358397B1 (fr) 2001-02-08 2002-01-12 Culbuteur pour mecanisme de distribution de moteur a combustion interne et dispositif d'ajustement/reajustement automatique du jeu des soupapes

Country Status (5)

Country Link
US (1) US6612278B2 (fr)
EP (1) EP1358397B1 (fr)
CN (1) CN1255620C (fr)
DE (2) DE10105807C1 (fr)
WO (1) WO2002063142A1 (fr)

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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 (de) * 2002-08-16 2007-11-08 Man Nutzfahrzeuge Ag Spielfreier Ventiltrieb für eine Brennkraftmaschine
US7112219B2 (en) 2002-11-12 2006-09-26 Myocor, Inc. Devices and methods for heart valve treatment
DE102012001633A1 (de) 2012-01-30 2013-08-01 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbare Ventiltriebanordnung
CN107676141A (zh) * 2017-11-15 2018-02-09 宁波里尔汽车技术有限公司 机械式气门间隙调整机构
CN115247582B (zh) * 2021-04-26 2023-07-21 北京福田康明斯发动机有限公司 一种调整发动机气门间隙的方法及装置

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US1948063A (en) * 1932-08-17 1934-02-20 Thompson Prod Inc Mechanical clearance regulator
DE621553C (de) * 1933-09-07 1935-11-12 Gen Motors Res Corp Vorrichtung zum Ausgleich des Spiels im Ventilantrieb von Brennkraftmaschinen u. dgl.
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 (fr) * 1957-06-26 1960-02-15 Ford Mécanisme de commande de soupape
FR1207502A (fr) 1958-06-13 1960-02-17 Herman Pneumatic Machine Co Perfectionnements apportés aux procédés et dispositifs pour tasser des moules de fonderie
US3658038A (en) * 1971-01-04 1972-04-25 Johnson Products Inc Tappet for overhead camshaft engine
JP2508062B2 (ja) * 1987-03-19 1996-06-19 三菱自動車工業株式会社 ロ−ラベアリングを用いたロツカア−ム
EP0331901B1 (fr) * 1988-02-05 1993-11-18 Dieter Voigt Entraînement de soupape pour une soupape à levée
DE3901966A1 (de) * 1988-02-05 1989-08-17 Volkswagen Ag Ventilantrieb fuer ein hubventil mit mechanischem ventilspielausgleich
DE4339433A1 (de) * 1993-11-18 1995-05-24 Bayerische Motoren Werke Ag Ventilhebel zur Steuerung eines Gaswechselventils einer Brennkraftmaschine, insbesondere Schlepphebel

Also Published As

Publication number Publication date
DE10105807C1 (de) 2002-05-08
CN1255620C (zh) 2006-05-10
WO2002063142A1 (fr) 2002-08-15
DE50212436D1 (de) 2008-08-14
EP1358397A1 (fr) 2003-11-05
US6612278B2 (en) 2003-09-02
US20030029404A1 (en) 2003-02-13
CN1457386A (zh) 2003-11-19

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