EP0224666B1 - Self adjusting hydraulic valve tappet - Google Patents

Self adjusting hydraulic valve tappet Download PDF

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Publication number
EP0224666B1
EP0224666B1 EP86112735A EP86112735A EP0224666B1 EP 0224666 B1 EP0224666 B1 EP 0224666B1 EP 86112735 A EP86112735 A EP 86112735A EP 86112735 A EP86112735 A EP 86112735A EP 0224666 B1 EP0224666 B1 EP 0224666B1
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EP
European Patent Office
Prior art keywords
sleeve
guide sleeve
oil
oil reservoir
inner piston
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
EP86112735A
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German (de)
French (fr)
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EP0224666A1 (en
Inventor
Dieter Goppelt
Dieter Schmidt
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.)
INA Waelzlager Schaeffler OHG
Original Assignee
INA Waelzlager Schaeffler OHG
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Filing date
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Publication of EP0224666A1 publication Critical patent/EP0224666A1/en
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Publication of EP0224666B1 publication Critical patent/EP0224666B1/en
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
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L1/25—Hydraulic tappets between cam and valve stem

Definitions

  • the invention relates to an automatically hydraulically adjusting valve tappet, according to the preamble of claim 1.
  • valve tappet If a valve tappet is installed without oil filling, or if it has emptied under unfavorable operating conditions, it will take a long time until this large-volume oil channel has completely filled up and is only then able to supply the central oil reservoir with oil. During this relatively long period of time, the well-known unpleasant rattling noise occurs, which is perceived as annoying.
  • plungers are installed in the predominant number of applications in a position inclined to the vertical, with the result that oil can only be sucked in from the outer annular oil reservoir through the annular oil channel, even if the highest point of the inclined lying lower edge of the sleeve extending from the bottom is covered by the oil present in the outer annular oil reservoir. Should this outer oil storage space e.g.
  • the invention has for its object to improve this known plunger by a simple structural measure so that it does not lose its advantages, but on the other hand avoids the disadvantages described.
  • the plunger shown in Fig. 1 consists of the cup-shaped housing 1, which consists of the hollow cylindrical wall 2 and the bottom 3 integral therewith.
  • this housing an inner part 4 is arranged, which is formed from the disc part 5 and the cylindrical guide sleeve 6.
  • the disk part 5 lies against the circumferential groove 8 formed in the hollow cylindrical wall and, on the other hand, is covered by the bead 9 formed out of the hollow cylindrical wall.
  • the hydraulic lash adjuster 10 is mounted, which consists of the outer piston 11, which is slidably guided in the guide sleeve 6, and which in turn slides and receives the inner piston 12 with tight play.
  • this has a central oil storage space 13, which is in fluid communication with an annular space 16 by means of the recess 14 in the inner surface 15 of the bottom 3, which is delimited by the inner piston 12 on the one hand and a sleeve 17 on the other, which starting from the bottom 3, it extends over the cylindrical guide sleeve 6 into the vicinity of the disk part 5.
  • the sleeve 17 is so dimen Sioned that it overlaps the guide sleeve 6 with its bore and has at least one circumferential point in the longitudinal direction extending groove-shaped formation 18 which together with the guide sleeve 6 delimits a longitudinal channel 19, via which oil from the outer annular oil reservoir 20 into the annular space 16 and from there can finally get into the central oil reservoir 13. From there, the oil is fed into the high-pressure oil chamber 22 in a known manner via the check valve 21. In order to ensure that the annular space 16 is sealed off from the annular oil storage space 20, the sleeve 17 can be connected to the inner surface 15 of the base 3 by the weld 23.
  • FIG. 2 differs from that of FIG. 1 only in that the sleeve 17 is also provided with a closed base 24 at its end facing the base 3. This makes it unnecessary to use additional measures such as e.g. Sealing welding, soldering, gluing or the like with respect to the annular oil reservoir 20. Rather, the sleeve 17 with its closed base 24 can simply be inserted loosely, because in operation it is pressed against the inner surface 15 of the base 3 by the inner piston 12.
  • a recess 25 is provided on at least one circumferential point of the inner piston 12 on its end face.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft einen sich selbsttätig hydraulisch einstellenden Ventilstößel, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an automatically hydraulically adjusting valve tappet, according to the preamble of claim 1.

Ein derartiger Ventilstößel ist bekannt geworden. Bei ihm umgibt die vom Boden ausgehende Hülse die Führungshülse mit allseitigem radialen Spiel, so daß sich zwischen diesen beiden Bauteilen ein Ölkanal mit ringförmigem Querschnitt ergibt. Diese Ausführung hat einerseits den Vorteil, daß das dem zentrischen Ölvorratsraum zugeführte Öl an einer unteren Stelle des äußeren ringförmigen Ölvorratsraumes angesaugt wird, womit sichergestellt ist, daß sich am oberen Ende des äußeren ringförmigen Ölvorratsraumes absetzende Luft nicht in den zentrischen Ölvorratsraum gesaugt werden kann. Diese bekannte Konstruktion weist jedoch gleichzeitig auch einen Nachteil auf, der in der ringförmigen Ausgestaltung des Ölkanales zwischen der vom Boden ausgehenden Hülse einerseits und der Führungshülse andererseits liegt. Wird z.B. ein Ventilstößel ohne Ölfüllung eingebaut, oder hat er sich unter ungünstigen Betriebsbedingungen entleert, dann dauert es sehr lange, bis sich dieser großvolumige Ölkanal vollständig aufgefüllt hat und erst dann in der Lage ist, den zentrischen Ölvorratsraum mit Öl zu versorgen. Während dieser relativ großen Zeitspanne tritt das bekannte unangenehme Klappergeräusch auf, welches als störend empfunden wird. Hinzu kommt, daß derartige Stößel in der überwiegenden Zahl der Anwendungsfälle in einer zur Senkrechten geneigten Lage eingebaut werden, was zur Folge hat, daß durch den ringförmigen Ölkanal erst dann Öl aus dem äußeren ringförmigen Ölvorratsraum angesaugt werden kann, wenn auch die höchste Stelle des geneigt liegenden unteren Randes der vom Boden ausgehenden Hülse von dem im äußeren ringförmigen Ölvorratsraum vorhandenen Öl überdeckt wird. Sollte dieser äußere Ölvorratsraum z.B. während einer Stillstandsphase teilweise leergelaufen sein, so kann es eine beträchtliche Zeit dauern, bis dieser wieder soweit mit Öl gefüllt ist, daß der ringförmige Ansaugquerschnitt des Ölkanales wieder vollständig von Öl bedeckt ist und damit nach Auffüllung dieses Ringkanales den zentrischen Ölvorratsraum ständig mit Öl versorgen kann. Eine Möglichkeit diese Probleme zu umgehen, besteht darin, ein Leerlaufen des Ölvorratsraumes generell zu verhindern, indem zwischen der Ölzulaufbohrung an der Wandung des Ventilstößels und dem Ölvorratsraum ein weiterer Ölvorratsraum vorgesehen wird, an dessen oberen Ende ein Überlauf zum eigentlichen Ölvorratsraum angeordnet ist. Damit ist zwar in der Regel eine Füllung des eigentlichen Ölvorratsraumes sichergestellt, bei zahlreichen Start-Stop-Zyklen, bei denen der zwischengeschaltete Ölvorratsraum gerade noch nicht bis zum Überlauf befüllt wird, kann dennoch der eigentliche Ölvorratsraum leergesaugt werden. Außerdem weist diese Lösung eine Verteuerung infolge der zusätzlichen Trennwand zwischen den Ölvorratsraumen auf (JP-A-59-65508).Such a valve lifter has become known. For him, the sleeve extending from the bottom surrounds the guide sleeve with radial play on all sides, so that an oil channel with an annular cross section results between these two components. On the one hand, this embodiment has the advantage that the oil supplied to the central oil reservoir is sucked in at a lower point of the outer annular oil reservoir, thereby ensuring that air settling out at the upper end of the outer annular oil reservoir cannot be sucked into the central oil reservoir. However, this known construction also has a disadvantage which lies in the annular configuration of the oil channel between the sleeve extending from the bottom on the one hand and the guide sleeve on the other. E.g. If a valve tappet is installed without oil filling, or if it has emptied under unfavorable operating conditions, it will take a long time until this large-volume oil channel has completely filled up and is only then able to supply the central oil reservoir with oil. During this relatively long period of time, the well-known unpleasant rattling noise occurs, which is perceived as annoying. In addition, such plungers are installed in the predominant number of applications in a position inclined to the vertical, with the result that oil can only be sucked in from the outer annular oil reservoir through the annular oil channel, even if the highest point of the inclined lying lower edge of the sleeve extending from the bottom is covered by the oil present in the outer annular oil reservoir. Should this outer oil storage space e.g. partially idle during a standstill phase, it can take a considerable amount of time until it is filled with oil again so that the ring-shaped intake cross-section of the oil channel is completely covered with oil and can therefore supply the central oil reservoir with oil after filling up this ring channel . One way to circumvent these problems is to generally prevent the oil reservoir from running dry by providing a further oil reservoir between the oil inlet bore on the wall of the valve lifter and the oil reservoir, an overflow to the actual oil reservoir being arranged at the upper end thereof. This generally ensures that the actual oil storage space is filled, but in the case of numerous start-stop cycles in which the intermediate oil storage space is not yet filled to the overflow, the actual oil storage space can still be sucked out. In addition, this solution is more expensive due to the additional partition between the oil reservoirs (JP-A-59-65508).

Der Erfindung liegt die Aufgabe zugrunde, durch eine einfache bauliche Maßnahme diesen bekannten Stößel so zu verbessern, daß er seine Vorteile nicht einbüßt, andererseits aber die beschriebenen Nachteile vermeidet.The invention has for its object to improve this known plunger by a simple structural measure so that it does not lose its advantages, but on the other hand avoids the disadvantages described.

Diese Aufgabe löst die Erfindung durch die kennzeichnenden Merkmale des Anspruchs 1. Dadurch, daß damit der Querschnitt des Längskanals auf einen kleinen Bruchteil des Querschnittes des ringförmigen Ölkanales bei dem bekannten Stößel reduziert wurde, wird einerseits erreicht, daß er sich auch im entleerten Zustand sehr rasch auffüllt. Andererseits wird er sich auch bei schräger Einbaulage des Stößels und unter Berücksichtigung der Tatsache, daß sich der Stößel im Betrieb um seine Längsachse dreht, aus statistischen Gründen nur äußerst selten in der höchsten denkbaren Position befinden, in welcher er denselben Nachteil wie bei der bekannten Stößelausführung hätte. In der überwiegenden Mehrzahl der Fälle wird sich dagegen dieser Längskanal während einer Stillstandphase in einer günstigeren Lage befinden.This object is achieved by the invention with the characterizing features of claim 1. Because the cross section of the longitudinal channel has been reduced to a small fraction of the cross section of the annular oil channel in the known tappet, it is achieved on the one hand that it can be very quickly emptied replenishes. On the other hand, even when the plunger is installed at an angle and taking into account the fact that the plunger rotates around its longitudinal axis during operation, for statistical reasons it is only very rarely in the highest conceivable position in which it has the same disadvantage as in the known plunger design would have. In the vast majority of cases, however, this longitudinal channel will be in a more favorable position during a standstill phase.

Zweckmäßige Ausführungsformen der Erfindung sind in den Unteransprüchen beschrieben.Advantageous embodiments of the invention are described in the subclaims.

In den Zeichnungen ist die Erfindung anhand von Längsschnitten durch unterschiedliche Stö- ßelausführungen beispielhaft dargestellt.The invention is illustrated by way of example in the drawings with the aid of longitudinal sections through different ram designs.

Der in Fig. 1 dargestellte Stößel besteht aus dem tassenförmigen Gehäuse 1, welches aus der hohlzylindrischen Wandung 2 und dem damit einstückigen Boden 3 besteht. In diesem Gehäuse ist ein Innenteil 4 angeordnet, welches aus dem Scheibenteil 5 und der zylindrischen Führungshülse 6 gebildet ist. An der Kontaktfläche 7 zwischen dem Außenumfang des Scheibenteiles 5 und der hohlzylindrischen Wandung 2 sind diese beiden Teile durch Einbördeln fest miteinander verbunden. Um eine flüssigkeitsdichte Verbindung zu erzielen, ist an dieser Stelle eine zusätzliche Schweißung, Lötung oder dergleichen möglich. Das Scheibenteil 5 legt sich zum Zwecke der Verbindung gegen die in die hohlzylindrische Wandung eingeformte Umfangsrille 8 und wird andererseits von der aus der hohlzylindrischen Wandung herausgeformten Wulst 9 überdeckt.The plunger shown in Fig. 1 consists of the cup-shaped housing 1, which consists of the hollow cylindrical wall 2 and the bottom 3 integral therewith. In this housing an inner part 4 is arranged, which is formed from the disc part 5 and the cylindrical guide sleeve 6. On the contact surface 7 between the outer circumference of the disk part 5 and the hollow cylindrical wall 2, these two parts are firmly connected to one another by crimping. In order to achieve a liquid-tight connection, additional welding, soldering or the like is possible at this point. For the purpose of connection, the disk part 5 lies against the circumferential groove 8 formed in the hollow cylindrical wall and, on the other hand, is covered by the bead 9 formed out of the hollow cylindrical wall.

In der Bohrung der zylindrischen Führungshülse 6 ist das hydraulische Spielausgleichselement 10 gelagert, das aus dem Außenkolben 11 besteht, der gleitend in der Führungshülse 6 geführt ist, und der andererseits wiederum gleitend und mit engem Spiel den Innenkolben 12 aufnimmt. Dieser weist an seinem dem Boden 3 zugewandten Ende einen zentrischen Ölvorratsraum 13 auf, welcher mittels der Ausnehmung 14 in der Innenfläche 15 des Bodens 3 in Flüssigkeitsverbindung mit einem Ringraum 16 steht, der durch den Innenkolben 12 einerseits und eine Hülse 17 andererseits begrenzt ist, welche ausgehend vom Boden 3 sich über die zylindrische Führungshülse 6 bis in die Nähe des Scheibenteiles 5 erstreckt. Die Hülse 17 ist dabei so dimensioniert, daß sie mit ihrer Bohrung die Führungshülse 6 außen übergreift und an wenigstens einer Umfangsstelle eine sich in Längsrichtung erstrekkende rinnenförmige Ausformung 18 aufweist, die zusammen mit der Führungshülse 6 einen Längskanal 19 begrenzt, über welchen Öl aus dem äußeren ringförmigen Ölvorratsraum 20 in den Ringraum 16 und von dort schließlich in den zentrischen Ölvorratsraum 13 gelangen kann. Von dort aus wird über das Rückschlagventil 21 das Öl in bekannter Weise in den Ölhochdruckraum 22 geführt. Um zu gewährleisten, daß der Ringraum 16 gegenüber dem ringförmigen Ölvorratsraum 20 abgedichtet ist, kann die Hülse 17 durch die Schweißung 23 mit der Innenfläche 15 des Bodens 3 verbunden sein.In the bore of the cylindrical guide sleeve 6, the hydraulic lash adjuster 10 is mounted, which consists of the outer piston 11, which is slidably guided in the guide sleeve 6, and which in turn slides and receives the inner piston 12 with tight play. At its end facing the bottom 3, this has a central oil storage space 13, which is in fluid communication with an annular space 16 by means of the recess 14 in the inner surface 15 of the bottom 3, which is delimited by the inner piston 12 on the one hand and a sleeve 17 on the other, which starting from the bottom 3, it extends over the cylindrical guide sleeve 6 into the vicinity of the disk part 5. The sleeve 17 is so dimen Sioned that it overlaps the guide sleeve 6 with its bore and has at least one circumferential point in the longitudinal direction extending groove-shaped formation 18 which together with the guide sleeve 6 delimits a longitudinal channel 19, via which oil from the outer annular oil reservoir 20 into the annular space 16 and from there can finally get into the central oil reservoir 13. From there, the oil is fed into the high-pressure oil chamber 22 in a known manner via the check valve 21. In order to ensure that the annular space 16 is sealed off from the annular oil storage space 20, the sleeve 17 can be connected to the inner surface 15 of the base 3 by the weld 23.

Die in Fig. 2 dargestellte Variante unterscheidet sich von der nach Fig. 1 lediglich dadurch, daß die Hülse 17 an ihrem dem Boden 3 zugewandten Ende ebenfalls mit einem geschlossenen Boden 24 versehen ist. Dadurch erübrigt es sich, die Hülse 17 mittels zusätzlicher Maßnahmen, wie z.B. Schweißen, Löten, Kleben oder dergleichen gegenüber dem ringförmigen Ölvorratsraum 20 abzudichten. Die Hülse 17 mit ihrem geschlossenen Boden 24 kann vielmehr einfach lose eingelegt werden, denn im Betrieb wird sie durch den Innenkolben 12 gegen die Innenfläche 15 des Bodens 3 gedrückt.The variant shown in FIG. 2 differs from that of FIG. 1 only in that the sleeve 17 is also provided with a closed base 24 at its end facing the base 3. This makes it unnecessary to use additional measures such as e.g. Sealing welding, soldering, gluing or the like with respect to the annular oil reservoir 20. Rather, the sleeve 17 with its closed base 24 can simply be inserted loosely, because in operation it is pressed against the inner surface 15 of the base 3 by the inner piston 12.

Um den Öldurchtritt aus dem Ringraum 16 in den zentrischen Ölvorratsraum 13 zu gewährleisten, ist hier an wenigstens einer Umfangsstelle des Innenkolbens 12 an dessen Stirnseite eine Ausnehmung 25 vorgesehen.In order to ensure the passage of oil from the annular space 16 into the central oil storage space 13, a recess 25 is provided on at least one circumferential point of the inner piston 12 on its end face.

Claims (4)

1. Self-adjusting hydraulic valve tappet arranged in a guide bore of a cylinder head of an internal combustion engine against one end face of which tappet a cam abuts and whose second end face bears against the end of a valve stem, the valve tappet comprising a cup-shaped housing (1) consisting of a hollow cyindrical wall (2) closed at one end by a bottom (3) against which the cam abuts from the outside and in which a guide sleeve (6) concentric with the hollow cylindrical wall (2) is arranged, which guide sleeve at its end away from the bottom opens into the centre of a disk member (5) whose outer periphery merges into the hollow cylindrical wall (2) of the housing (1), the other end of the guide sleeve (6) being at a distance from the bottom (3) and the actual hydraulic clearance compensation element (10) being longitudinally slidably guided in the guide sleeve (6) and being made up of an inner piston (12) and an outer piston (11) overlapping this, the two being longitudinally slidably guided in each other and together delimiting an oil pressure chamber (22) connected with a central oil reservoir (13) through a bore in the inner piston (12) closed by a non-return valve (21), the oil reservoir (13) being arranged in the inner piston (12) and delimited on one side by the wall of the inner piston (12) and on the other, by the inner surface (15) of the bottom (3) of the housing (1) against which an end face of the inner piston (12) bears, whereas the outer piston (11) is mounted longitudinally slidably in the cylindrical guide sleeve (6) and bears with its closed end against the end of the valve stem, the hollow cylindrical wall (2), the guide sleeve (6), the hydraulic clearance compensation element (10), the bottom (3) and the disk member (5) delimiting an annular oil reservoir (20) supplied with oil through a bore leading to the outside, and a sleeve (17) starting from the bottom (3) and sealed at its end towards the bottom (3) against the annual oil reservoir (20) and overlapping the guide sleeve (6) and extnding to near the disk member (5) is provided, the sleeve (17) and the inner piston (12) delimiting an annular space (16) connected through an oil passage (14, 25) to the central oil reservoir (13), the annular space (16) being in fluid communication with the oil reservoir (20) through an oil channel (19) formed between the sleeve (17) and the guide sleeve (6), characterized in that the oil channel is formed as a longitudinal channel (19) arranged at one single peripheral point between the sleeve (17) and the guide sleeve (6) and allowing the passage of oil from the annular oil reservoir (20) into the annular space (16).
2. Valve tappet according to Claim 1, characterised in that the sleeve (17) is a hollow cylindrical section of tube open at both ends, one of which bears against the bottom (3) of the housing (1) from the inside and is joined to it by a sealed joint (e.g. by soldering, welding, bonding or the like).
3. Valve tappet according to Claim 1, characterised in that the sleeve (17) is a section of tube closed at one end by a bottom (24), bearing against the bottom (3) of the housing (1) from the inside.
4. Valve tappet according to Claim 1 or 2, characterised in that the bore of the sleeve (17) bears against the outer peripheral surface of the guide sleeve (6) and that this sleeve (17) has at one point of its periphery a groove-shaped formation (18) extending in the longitudinal direction and delimiting together with the guide sleeve (6) a longitudinal channel (19).
EP86112735A 1985-11-29 1986-09-15 Self adjusting hydraulic valve tappet Expired - Lifetime EP0224666B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3542192 1985-11-29
DE19853542192 DE3542192A1 (en) 1985-11-29 1985-11-29 AUTOMATICALLY HYDRAULICALLY ADJUSTING VALVE

Publications (2)

Publication Number Publication Date
EP0224666A1 EP0224666A1 (en) 1987-06-10
EP0224666B1 true EP0224666B1 (en) 1990-04-11

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ID=6287144

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86112735A Expired - Lifetime EP0224666B1 (en) 1985-11-29 1986-09-15 Self adjusting hydraulic valve tappet

Country Status (4)

Country Link
US (1) US4721076A (en)
EP (1) EP0224666B1 (en)
JP (1) JPH0647925B2 (en)
DE (2) DE3542192A1 (en)

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DE3623638C2 (en) * 1986-07-12 1994-02-24 Schaeffler Waelzlager Kg Automatically hydraulic valve lifter
DE3637906A1 (en) * 1986-11-06 1988-05-19 Schaeffler Waelzlager Kg AUTOMATICALLY HYDRAULICALLY ADJUSTING VALVE
DE3810436A1 (en) * 1988-03-26 1989-10-12 Schaeffler Waelzlager Kg AUTOMATICALLY HYDRAULICALLY ADJUSTING VALVE
DE3828635A1 (en) * 1988-08-24 1990-03-08 Daimler Benz Ag METHOD FOR PRODUCING CUPS FOR LIFTING PISTON MACHINES
US4924821A (en) * 1988-12-22 1990-05-15 General Motors Corporation Hydraulic lash adjuster and bridge assembly
DE8902780U1 (en) * 1989-03-08 1989-04-20 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Self-adjusting hydraulic valve tappet
IT1230012B (en) * 1989-04-20 1991-09-20 Eaton Automotive Spa HYDRAULIC TAPPET WITH OIL SUCTION DUCT, FROM THE EXTERNAL TANK TO THE INTERNAL TANK WITHOUT INCLUSIONS OF AIR BUBBLES, MADE BY MECHANICAL PROCESSING.
IT1229355B (en) * 1989-05-23 1991-08-08 Eaton Automotive Spa HYDRAULIC TAPPETS WITH OIL CIRCULATION ALONG A 360 DEVELOPING PATH [ON TWO LEVELS.
DE3920729A1 (en) * 1989-06-24 1991-01-10 Gmb Giesserei & Maschinenbau B CUPS FOR BOTTLE VALVES
DE4332110A1 (en) * 1993-09-22 1995-03-23 Schaeffler Waelzlager Kg Tappet with hydraulic valve clearance adjustment
DE19630443A1 (en) * 1996-07-27 1998-01-29 Schaeffler Waelzlager Kg Zero backlash hydraulic tappet for internal combustion engine
US5758613A (en) * 1997-01-30 1998-06-02 Eaton Corporation Hydraulic lash adjuster and biased normally open check valve system therefor
DE102006045017A1 (en) * 2006-09-23 2008-03-27 Schaeffler Kg Double flow hydraulic supporting unit for adjustable cam follower, has path led axially upwards from passage to pressure piston into deviating section between bases of pot shaped sections

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DE2929890A1 (en) * 1979-07-24 1981-02-12 Audi Nsu Auto Union Ag IC engine valve tappet - is of light metal or alloy and has wear-resistant coating on rubbing surfaces
US4373477A (en) * 1980-12-29 1983-02-15 Eaton Corporation Lash adjuster with plunger retainer
JPS5965508A (en) * 1982-10-08 1984-04-13 Aisin Seiki Co Ltd Hydraulic lifter for ohc direct type device
JPS60182301A (en) * 1984-02-29 1985-09-17 Atsugi Motor Parts Co Ltd Direct-acting type tappet mechanism
DE3412153A1 (en) * 1984-03-31 1985-10-10 Motomak Motorenbau, Maschinen- u. Werkzeugfabrik, Konstruktionen GmbH, 8070 Ingolstadt METHOD FOR FASTENING A FUNNEL-SHAPED GUIDE PART IN THE HOLE WALL OF THE CUP-SHAPED HOUSING OF A SELF-ACTUATING HYDRAULICALLY ADJUSTING VALVE TAPE
DE3412175A1 (en) * 1984-03-31 1985-10-10 Motomak Motorenbau, Maschinen- u. Werkzeugfabrik, Konstruktionen GmbH, 8070 Ingolstadt CUP-SHAPED HOUSING OF A SELF-ACTUATING HYDRAULICALLY ADJUSTING VALVE TOLDER FOR INTERNAL COMBUSTION ENGINES WITH OVERHEAD CAMSHAFT
JPS611606U (en) * 1984-06-11 1986-01-08 日産自動車株式会社 hydraulic lifter
DE3437478A1 (en) * 1984-10-12 1986-04-17 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach AUTOMATICALLY HYDRAULICALLY ADJUSTING VALVE
DE3500425A1 (en) * 1985-01-09 1986-07-10 Motomak Motorenbau, Maschinen- u. Werkzeugfabrik, Konstruktionen GmbH, 8070 Ingolstadt HYDRAULIC CUPS FOR COMBUSTION ENGINES

Also Published As

Publication number Publication date
EP0224666A1 (en) 1987-06-10
DE3670338D1 (en) 1990-05-17
JPS62131906A (en) 1987-06-15
DE3542192A1 (en) 1987-06-04
US4721076A (en) 1988-01-26
JPH0647925B2 (en) 1994-06-22

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