EP0030781B1 - Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung - Google Patents

Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung Download PDF

Info

Publication number
EP0030781B1
EP0030781B1 EP19800302755 EP80302755A EP0030781B1 EP 0030781 B1 EP0030781 B1 EP 0030781B1 EP 19800302755 EP19800302755 EP 19800302755 EP 80302755 A EP80302755 A EP 80302755A EP 0030781 B1 EP0030781 B1 EP 0030781B1
Authority
EP
European Patent Office
Prior art keywords
tappet
plunger
wall
hub
fluid
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
Application number
EP19800302755
Other languages
English (en)
French (fr)
Other versions
EP0030781A1 (de
Inventor
Stephen Mark Buente
William Thomas Mihalic
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.)
Eaton Corp
Original Assignee
Eaton Corp
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=22281041&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0030781(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of EP0030781A1 publication Critical patent/EP0030781A1/de
Application granted granted Critical
Publication of EP0030781B1 publication Critical patent/EP0030781B1/de
Expired legal-status Critical Current

Links

Images

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

  • This invention concerns a bucket tappet for the valve gear of an internal combustion engine, which valve gear is of the direct-acting type wherein one end of the tappet is contacted by an engine cam and the other end contacts a stem of a combustion chamber valve.
  • valve gear of the cam-over-valve type In designing valve gear for internal combustion engines operating at speeds in excess of 5,000 rpm, it has been found desirable to employ valve gear of the cam-over-valve type.
  • Valve gear of this type is known as direct-acting valve gear and employs a tappet having one end contacting the engine cam shaft with the other end of the tappet in direct contact with the end of the stem of the combustion chamber valve.
  • Direct acting valve gear offers the advantage of low mass, fewer working parts and higher stiffness due to the elimination of the rocker arm and/or push rods. Low mass and high stiffness result in a high natural resonant frequency which allows the valve gear to attain higher rpm's before valve mis-motion occurs.
  • Direct acting valve gear also permits the use of lighter valve spring loads for a given valve motion and engine speeds as compared with those used in other valve gear arrangements.
  • the low mass and high stiffness of the system also permits valve lift velocities and accelerations which increase the area under the valve lift curve and thus provide increased specific engine output.
  • a direct acting valve gear arrangement offers the additional advantage of permitting rotation of the cam contacting surfaces as the lifter rotates which is not possible with rocker arm type valve gear arrangements. Direct acting valve gear arrangements, therefore, allow higher permissible cam contact stresses.
  • cam profile for other overhead cam valve gear arrangements with high lift accelerations and velocities is more complex than that required for direct acting valve gear.
  • the simpler cam profile requirement of direct acting valve gear results in less manufacturing difficulties and less cost in the valve gear when high velocities and accelerations are desired.
  • a known hydraulic tappet for direct-acting valve gear such as that shown and described in U.S. Patent 3,509,858 to Scheibe et al, employs a body, or bucket, formed as an integral unit having a reservoir provided by an undercut in the plunger guide bore formed in the bucket.
  • the necessity of the undercutting requires a relatively large plunger guide bore in the body which in turn results in a reduced hydraulic pressure upper operating limit.
  • the undercut reservoir is reduced in volume and the mass of the tappet is increased, resulting in greater inertia.
  • This tappet design is in any event inherently of relatively high inertia and the undercut annular reservoir is of small volume. Such a tappet is not suitable for use in engines running at over 5,000 RPM.
  • a further problem encountered in the design of hydraulic bucket tappets has been the necessity of providing precision sliding surfaces on the outer diameter of the plunger and the inner periphery of the plunger guide bore formed in the bucket. Such precision surfaces are required in order to provide control of leakdown from the high pressure hydraulic chamber in the tappet where this sliding interface is employed as the leakdown control surface, as, for example, in the tappet described in German Patent 1,914,693.
  • the high pressure hydraulic fluid chamber for effecting lash adjustment is disposed at or near the upper level of the fluid reservoir and consequently is susceptible to retention of trapped air.
  • This requirement for leakdown control has heretofore required extremely tight tolerances on the dimensions of the bucket bore and plunger diameter.
  • the necessity of forming the plunger guide bore in the bucket to tight tolerances has resulted in costly scrap losses if such operations are defectively performed.
  • DE OS 1,808,000 shows in Figure 2 a design intended to provide a low height and an adequate reservoir volume in a tappet suitable for high-RPM engines.
  • the plunger is fitted over, and is guided and supported by, a cylindrical extension fixed to the underside of the top of the tappet.
  • An annular first reservoir portion surrounds the plunger and a second, central reservoir portion is located within the cylindrical extension and above the high pressure chamber, which is in the lower end of the plunger.
  • the design requires separate forming of the cylindrical extension and the tappet top, and then fixing the two together in the central region of the tappet top such as by welding. This is undesirable since in the same region the tappet top needs to be both fatigue resistant and hardened for wear resistance. Fluid is retained in the tappet by means of a plate 7a and a sealing ring 25 which, together, are merely stated to perform a sealing function.
  • the invention seeks to provide a bucket tappet for high-RPM engines which not only is relatively low and light but also can be manufactured with reduced scrap losses and without having to weld or otherwise fix components near the centre of the top of the tappet.
  • a bucket tappet for use in the valve gear of an internal combustion engine which is capable of operating at speeds in excess of 5,000 RPM, which valve gear is of the direct acting type wherein one end of the tappet is contacted by an engine cam and the other end is in direct contact with a stem of a combustion chamber valve, the tappet comprising:
  • said hub being maintained in fixed relation to the top, but with its upper end axially separated from said top, by means of said web which extends between the hub and the tubular outer wall and connects the hub to the tubular outer wall so as to form the sole structural support for the hub.
  • the construction of the present tappet provides a low profile height for minimizing the distance required between the engine cam and the end of the combustion chamber valve stem, and relatively low mass and inertia.
  • the construction also provides for a relatively large diameter and adequate reservoir of fluid formed by the central reservoir portion within the piston in conjunction with the annular reservoir portion. Supporting the plunger through the web and hub avoids the need to fix any plunger support to the tappet top, and the provision of the leakdown surfaces on the plunger and relatively small diameter piston helps to enable more accurate machining of those surfaces and results in less scrap material due to any machining inaccuracies.
  • the bucket tappet indicated generally as 10 is slidably received in a guide bore 12 provided in the cylinder head H of the engine structure.
  • a cam shaft 14 having a cam lobe 16 contacts the upper end or cam face of the tappet.
  • a typical combustion chamber valve 20 is shown seated on a valve seating surface formed in the cylinder head H with the stem portion 22 of the valve extending substantially vertically upward through a valve guide 24 formed in the cylinder head H, with the upper end 26 of the valve stem contacting the lower end of the tappet.
  • valve spring 28 having its lower end registering against the exterior of the upper portion of the valve guide 24 and its upper end in contact with a retainer 30 secured to the valve stem adjacent its upper end and retained thereon in a suitable manner as, for example, by the use of a split keeper 32 which is well known in the art.
  • the presently preferred embodiment of the tappet 10 is shown wherein the body, indicated generally at 40, is shown as formed preferably integrally with an outer tubular wall 42 having a transverse web 44 extending generally radially inwardly from the inner periphery of the outer tubular wall at a location intermediate the ends thereof.
  • the web 44 has formed preferably integrally therewith a tubular hub 46 formed about the inner periphery of the web 44 with the hub 46 extending axially from the web in a downward direction with respect to Figure 3.
  • the hub 46 has the inner periphery thereof extending in generally parallel relationship to the outer periphery of the tubular wall 42.
  • the outer periphery of the tubular wall 42 is sized to be received in the tappet guide bore 12 (see Fig. 1) in a generally closely fitting relationship.
  • the outer wall, web and hub have been described as preferably formed integrally, it will be understood that such portions may be formed separately and the body formed by joining of those portions, as for example, by weldment, such as fusion or brazing.
  • a cam face member 18 having a relatively thin disc-shaped configuration is joined about the outer periphery thereof with the upper end of the tubular outer wall 42 in a suitable manner, as for example, by laser fusion weldment.
  • a fluid by-pass recess 43 is formed in the underface of member 18, the function of which will be hereinafter described.
  • the tappet cam face member is formed of a suitable alloy steel as, for example, an alloy containing a desired amount of chromium and is suitably hardened for wear resistance.
  • the tubular outer wall in the presently preferred practice is formed of a suitable iron base material as, for example, steel or cast iron.
  • the cam face member is formed of steel having a hardened surface, it will be understood that other metals, for example, nickel alloys may be used, or hardenable cast iron or ceramic materials or cermets may be employed if desired.
  • the hub 46 has received therein a plunger 49 having the outer periphery 50 thereof in sliding closely fitting relationship with the interior 48 of the hub.
  • the plunger 49 has the transverse face 52 thereof, or lower face with respect to Fig. 3, adapted for driving engagement with the end 26 (see Fig. 1) of the combustion chamber valve stem.
  • the plunger is formed of steel with end face 52 suitably hardened for wear resistance.
  • the outer periphery 50 of the plunger has an annular shoulder 54 formed thereon at the intersection with the end face 52.
  • An annular retainer 56 is received on the end of the hub 46 and engaged therewith, preferably in a groove 58 formed in the outer periphery of hub 46.
  • the inner periphery 60 of the retainer has a diameter intermediate that of the hub interior 48 and the inner diameter of shoulder 54 such that the retainer 56 serves to limit the downward motion of the plunger 49.
  • the plunger 49 has a precision cylindrical bore 62 formed in the upper end thereof with the lower end of the bore terminating in a shouldered flat bottom.
  • the precision bore 62 has slidably received therein in very closely fitting relationship a piston 64, the outer periphery 66 thereof being of precision diameter and smoothness so as to provide control of the leakdown or passage of pressurized engine lubricant therebetween.
  • the piston 64 is formed of a suitable steel material.
  • the piston 64 has a fluid passage 68 formed vertically and preferably centrally therethrough with a counterbore 70 formed therein.
  • the bottom end of the passageway 68 has a counterbore 71 provided in the lower end of the piston 64 which counterbore has a flat bottom 73 which intersects the passageway 68 in an annular seat 74.
  • a check-ball 72 rests against the annular seat 74, and is, as known in the art biased thereagainst by a suitable expedient as, for example, a conical check-ball spring 76 to provide a one-way valve.
  • the check-ball 72 is retained by a cage 78 which has an outwardly extending flange 80 received in counterbore 71 and retained therein by suitable means as, for example, a press fit.
  • the cage in the presently preferred practice has a central aperture 75 into which the check-ball 72 is partially received in the valve fully open position as shown in Fig. 4.
  • the subassembly of the check-ball, cage and piston is biased upwardly by a plunger spring 82 having its upper end registering against the flange 80 of the check-ball cage and its lower end contacting the bottom of the plunger.
  • the area surrounding the plunger 49 above the web 44 and bounded by the under surface of cam face member 18 comprises a first portion 83 of a fluid reservoir which is communicated with the region externally of the outer wall 42 by a passageway 84 provided through the outer tubular wall of the tappet body and the web 44.
  • the by-pass recess 43 functions to maintain a second portion 85 of the reservoir bounded by piston counterbore 70 and the underface of member 18 in continuous fluid communication with the first portion 83 of the reservoir. It will be understood the piston is maintained in the upward extreme position and against the undersurface of member 18, as illustrated in Figures 3 and 4 by spring 82 and the hydraulic pressure in chamber 86 defined between the plunger 49 and the piston 64.
  • the fluid retained in the second portion 85 of the fluid reservoir supplies the one-way valve upon engine start-up in the event that during periods of engine inactivity, fluid has drained from the first portion 83 of the reservoir.
  • the chamber 86 below the check-ball 72 and seat 74 and bounded by the bore of the plunger, and the bottom of the plunger comprises a high pressure fluid chamber for retaining therein fluid entering through passage 68 upon opening of the check-ball 72.
  • the combustion chamber valve is biased to a closed position by spring 28 and upon rotation of the cam shaft in timed relationship to the events of the combustion chamber to the position shown in solid outline in Figure 1, the upper surface of the tappet is registered against the base circle portion of the cam with the lobe 16 oriented so as not to contact the cam face member 18 of the tappet.
  • the cam load contacts the cam face member 18 of the tappet, causing the tappet to move downwardly thereby opening the combustion chamber valve.
  • the valve event is complete and the valve is reseated on the valve seat.
  • the plunger spring 82 In operation, with the engine cam lobe 16 in the position shown in Fig. 1, the plunger spring 82, aided by hydraulic pressure, maintains the upper end of piston 64 in contact with the undersurface of cam face member 18 and urges the plunger 49 in the downward direction until the end face 52 thereof contacts the upper face 26 of the valve stem 22 thereby eliminating lash in the valve gear.
  • This causes expansion of chamber 86 which draws open the check-ball 72 to the position shown in Fig. 4 permitting fluid to flow into chamber 86.
  • the check-ball 72 closes under the biasing spring 76.
  • an alternate embodiment of the tappet is shown generally at 100 as employing a tubular outer wall 102 having an inwardly extending web 104 integrally formed therewith and a central tubular hub 106 formed integrally with the web 104.
  • a plunger 108 is slidably received in the hub 106.
  • the plunger has a hydraulic piston and one-way valve similar to that of embodiment of Fig. 3, and the outer tubular wall 102 has the one end thereof closed by a cam face member 107.
  • the plunger 108 in the embodiment of Fig. 5 has a circumferential groove 110 formed about the periphery thereof with a radially compressible-expandable generally C-shaped snap-ring 112 received therein.
  • the plunger assembly with the ring 112 received thereon is piloted into the inner periphery of the hub 106, the ring 112 is then compressed such that its outer circumference is less than the inner periphery of the hub.
  • the plunger is then moved upward with respect to Fig. 5 until the snap ring 112 passes through the hub 106 and then is free to expand slightly so as to retain the plunger assembly from removal from the hub.
  • the embodiment of Fig. 5 eliminates the need for the forming of a groove, such as groove 58, in the wall of the hub 46 (see Fig. 3) which results in difficult manufacturing operations in forming such groove particularly when the outer diameter of the body is less than 35 mm.
  • the embodiment of Fig. 5 results in a tappet assembly in which the plunger subassembly is potentially more difficult to remove.
  • FIG. 6 a further alternate embodiment of the invention is illustrated wherein portions of the tappet indicated generally at 120 are shown.
  • the body of the tappet of Fig. 6 has an outer tubular wall 122 and a transverse web 124 having integrally formed therewith a central tubular hub 126 extending axially downwardly from the web 124.
  • the inner periphery of the hub 126 has a circumferential groove 128 formed therein adjacent the lower end thereof with a retaining means in the form of a snap ring 130 received therein for retaining the plunger 132 in the hub.
  • an alternate embodiment of the tappet 140 is illustrated having an outer tubular wall 141 closed at the upper end thereof by a transverse end wall 142 providing a cam face member and having the upper surface thereof hardened for contacting a cam.
  • the transverse wall 142 is preferably formed integrally with the outer wall 141 and of a suitable iron base material such as a readily formable and hardenable steel.
  • the outer wall 141 has a preferably annular rib 144 extending from the inner surface thereof intermediate the ends of the outer wall and has a circumferential groove 147 formed in its inner periphery and spaced vertically downward in Figure 7 from the rib 144.
  • annular member 146 formed of a suitable iron base material as, for example, an unhardened carbon steel, is received in the inner periphery of the outer wall 141 with the upper surface of annular member 146 registering against the lower surface of annular rib 144.
  • the annular member 146 forms a central web as in the previous embodiments and has a downwardly extending annular hub 148 formed integrally therewith and centrally disposed with respect thereto which hub 148 has received therein a suitable hydraulic lash-adjusting assembly indicated generally at 150 and similar to the assembly shown and described hereinabove with respect to Figures 3, 4 and 5.
  • the hydraulic lash-adjusting assembly 150 is retained in the inner periphery of hub 148 by deformation of the lower edge of the hub inwardly to form a lip 152.
  • the outer periphery of annular member 146 has an annular wall 154 extending downwardly with respect to Figure 7 from the outer periphery of the annular member 146 and along the inner periphery of the outer wall 141 of the tappet body.
  • the lower edge of wall 154 is deformed outwardly into the groove 147 to retain the annular member 146 registered against the undersurface of rib 144 and to prevent removal of the annular member 146 from the tappet body.
  • the annular member 146 thus defines the first portion 156 of the hydraulic fluid reservoir similar to the portion 83 of the embodiment of Figure 3.
  • the function of the hydraulic lash-adjusting assembly 150 in tappet 140 is otherwise identical to that described hereinabove with respect to the embodiments of Figures 2 through 5.
  • the embodiment of Figure 7 provides a simplified structure for the bucket or tappet body; however, a separate insert is required to provide for the first portion of the fluid reservoir and the supporting hub for the lash-adjusting assembly.
  • the present invention provides a unique bucket tappet for use in direct acting valve gear of internal combustion engines and it is particularly suitable for operating speeds in excess of 5,000 rpm.
  • the present tappet employ a hardened steel member attached over one end of a tubular outer wall of the tappet body, for providing the cam face of the tappet.
  • the tubular outer wall has, preferably formed integrally therewith, an inwardly extending web disposed intermediate the ends of the tubular outer wall, with the web having formed integrally therewith a centrally disposed tubular hub for receiving the hydraulic lash adjusting assembly.
  • the plunger assembly is retained preferably by retaining means engaging the tubular hub or alternatively, by a snap ring provided in the outer periphery of the plunger.
  • the described tappet provides the lash adjustment by a precision fit of a piston in a bore formed in the plunger slidably received in the hub, and thus eliminates the need for precision fitting leakdown control surfaces on the interior of the tappet hub.
  • the area surrounding the plunger between the web and tubular outer wall of the body and the cam face member provides a first portion of a reservoir and a cavity in the piston provides a second portion of the reservoir for fluid to supply the one-way valve of the hydraulic lash adjusting assembly.
  • the external retaining means in the preferred embodiment permits ease of manufacturing and ready removal of the hydraulic plunger assembly for cleaning and/or parts replacement.
  • the fluid pressure chamber is located near or below the lowest level of the two-part fluid reservoir to provide a convenient escape path for any trapped air.

Landscapes

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

Claims (14)

1. Tassenstößel (10) zur Verwendung im Ventiltrieb einer Verbrennungsmachine, die in der Lage ist bei Drehzahlen oberhalb 5000 Umdrehungen pro Minute zu arbeiten, wobei der Ventiltrieb zur direktarbeitenden Bauart gehört, wo ein Ende des Stößels (10) durch einen Maschinennocken (16) kontaktiert wird und das andere Ende in direktem Kontakt mit einem Schaft (22) eines Verbrennungskammerventils (20) steht, wobei der Stößel (10) folgendes aufweist:
- eine röhrförmige Außenwand (42; 102; 122; 141
- ein sich quer zur Außenwand am oberen Ende des Stößels erstreckender und zur Kontaktierung des Maschinennockens geeigneter Oberteil (18; 107; 142),
- ein Plunger (49; 108; 132) angeordnet innerhalb und axial gleitend bezüglich der Außenwand, wobei der Plunger an seinem unteren Ende eine Endwand (52) zum Kontaktieren des Ventilschaftes besitzt,
- ein ringförmiger erster Teil (83) eines Strömungsmittelreservoirs angeordnet radial zwischen der rohrförmigen Außenwand (42; 102; 122; 141) und dem Plunger (49; 108; 132) und axial zwischen dem Oberteil (18; 107; 142) und einem Steg (44; 104; 124; 146), der den Boden des Ringteils des Reservoirs bildet, wobei die Radialerstreckung des ersten Teils im wesentlichen die gleiche ist wie die des Stegs,
- Durchlaßmittel (84) zur Lieferung von Strömungsmittel an den Ringteil des Reservoirs,
- einen mittigen zweiten Teil (85) des Reservoirs in Strömungsmittelverbindung mit dem ersten Teil,
- eine Strömungsmitteldruckkammer (86) innerhalb des Plungers und zwar angeordnet nahe oder unterhalb des untersten Niveaus der erwähnten beiden Teile des Reservoirs,
- ein Einwegventil (72; 74) betätigbar um einen Strömungsmittelfluß hindurchzulassen, und zwar von dem mittigen zweiten Teil (85) des Reservoirs in die Strömungsmitteldruckkammer (86) bei Bewegung des Pungers (49; 108; 132) in einer Richtung, die bestrebt ist, die Kammer (86) auszudehnen und um den umgekehrten Strömungsmittelfluß von der Strömungsmitteldruckkammer (86) dahindurch zu verhindern, bei Bewegung des Plungers (49; 108; 132) in einer Richtung, die bestrebt ist, die Strömungsmitteldruckkammer zu verkleinern,

dadurch gekennzeichnet, daß ein am Oberteil (18; 107; 142) nicht befestigter Kolben (64) gleitend in dem Plunger (49; 108; 132) aufgenommen ist und mit dem Plunger zur Definition der Strömungsmitteldruckkammer (86) zusammenarbeitet, wobei Vorspannmittel (82) zwischen dem Plunger und dem Kolben angordnet sind, um den Plunger und den Kolben in eine Richtung von einander weg vorzuspannen,
daß der Kolben (64) in den Plunger (49; 108; 132) in einer Art und Weise paßt, daß ein gesteuertes Leck von der Strömungsmitteldruckkammer (86) vorgesehen wird, und zwar beim Anlegen einer Axialbelastung an den Kolben (64), die bestrebt ist, den Kolben (64) in eine Richtung zu drücken, um das Strömungsmittel in der Strömungsmitteldruckkammer (86) zusammenzudrücken,
daß der Mittelteil des Reservoirs innerhalb des Kolbens (64) zwischen dem Kolben und dem Oberteil (18; 107; 142) angeordnet ist, und
daß der Plunger in einer im ganzen rohrförmigen Nabe (46; 106; 126; 148) aufgenommen ist getragen innerhalb der Außenwand und sich im ganzen parallel dazu erstreckend,
wobei die Nabe in fester Beziehung zum Oberteil (18; 107; 142) gehalten wird, aber mit ihrem oberen Ende axial getrennt vom Oberteil, und zwar mittels des Steges der sich zwischen der Nabe und der rohrförmigen Außenwand erstreckt und die Nabe mit der rohrförmigen Außenwand verbindet, um so die einzige bauliche Halterung für die Nabe zu bilden.
2. Stößel nach Anspruch 1, dadurch gekennzeichnet, daß die Nabe (46; 106; 126; 148) gesondert von dem Oberteil (18; 107; 142) ausgebildet ist.
3. Stößel nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Steg (44; 104; 124; 146) sich nach innen von der Außenwand (42; 102; 122; 141) aus erstreckt, und zwar zischen den Enden der Außenwand (42; 102; 122; 141).
4. Stößel nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Steg (44; 104; 124) integral mit der Außenwand (42; 102; 122) gebildet ist, und daß die Nabe (46; 106; 126) integral mit dem Steg (44; 104; 124) ausgebildet ist.
5. Stößel nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Steg (146) und die Nabe (148) durch ein ringförmiges Glied angeordnet innerhalb der Außenwand (141) vorgesehen sind.
6. Stößel nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Oberteil (18; 107) ein scheibenförmiges Glied aufweist angeordnet über einem Ende der Außenwand (42; 101; 122) und befestigt daran um den Umfang derselben herum.
7. Stößel nach einem der Ansprüche 1 bis 3 oder 5, dadurch gekennzeichnet, daß der Oberteil (142) integral mit der Außenwand (141) ausgebildet ist.
8. Stößel nach irgendeinem vorhergehenden Anspruch, gekennzeichnet durch Haltemittel (56; 112; 130; 152) zum Halten der Plungeranordnung (49; 64) in der Nabe (46; 106; 126; 148).
9. Stößel nach Anspruch 8, dadurch gekennzeichnet, daß die Haltemittel ein Ringglied (56) aufweisen, welches mit dem Außenumfang der Nabe (46) in Eingriff steht.
10. Stößel nach Anspruch 8, dadurch gekennzeichnet, daß die Haltemittel ein Ringglied (56) aufweisen, welches über dem Ende der Nabe (46) entfernt von dem Oberteil (18) aufgenommen ist.
11. Stößel nach Anspruch 8, dadurch gekennzeichnet, daß die Nabe (46) eine Umfangsnut (58) aufweist ausgebildet im Außenumfang derselben und ferner dadurch gekennzeichnet, daß die Haltemittel ein ringförmiges Federclip (56) aufweisen, welches mit der Umfangsnut (58) in Eingriff steht.
12. Stößel nach Anspruch 8, dadurch gekennzeichnet, daß der Plunger (40) eine Umfangsausnehmung (110) aufweist, und daß die Haltemittel ein Ringglied (112) aufgenommen in der Ausnehmung (110) aufweisen.
13. Stößel nach Anspruch 8, dadurch gekennzeichnet, daß die Nabe (148) mit einer Lippe (152) gebildet ist, welche die Haltemittel vorsieht.
14. Stößel nach irgendeinem vorhergehenden Anspruch, dadurch gekennzeichnet, daß die Durchlaßmittel einen Strömungsmitteldurchlaß (84) durch die Außenwand (42; 102; 122; 141) aufweisen und zwar zur Verbindung des Außenumfangs der Außenwand (42; 102; 122; 141) mit dem Strömungsmittelreservoir (83; 85; 156; 176).
EP19800302755 1979-12-05 1980-08-11 Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung Expired EP0030781B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10068979A 1979-12-05 1979-12-05
US100689 1979-12-05

Publications (2)

Publication Number Publication Date
EP0030781A1 EP0030781A1 (de) 1981-06-24
EP0030781B1 true EP0030781B1 (de) 1989-12-13

Family

ID=22281041

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800302755 Expired EP0030781B1 (de) 1979-12-05 1980-08-11 Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung

Country Status (4)

Country Link
EP (1) EP0030781B1 (de)
JP (1) JPS5683508A (de)
BR (1) BR8005733A (de)
DE (1) DE3072169D1 (de)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373477A (en) * 1980-12-29 1983-02-15 Eaton Corporation Lash adjuster with plunger retainer
DE3203439A1 (de) * 1982-02-02 1983-08-11 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Verfahren zum fluessigkeitsdichten befestigen des aeusseren randes eines flanschartigen blechteiles in der bohrung eines ventilstoessels und vorrichtung zur durchfuehrung des verfahrens
EP0375792B1 (de) * 1982-03-29 1995-01-18 Alfred Anthony Black Verstellbarer Ventilfederteller für eine Brennkraftmaschine
JPS5923008A (ja) * 1982-07-28 1984-02-06 Fuji Valve Kk 油圧タペットの本体成形法
JPS5934005U (ja) * 1982-08-30 1984-03-02 トヨタ自動車株式会社 内燃機関の油圧リフタ
JPS5949705U (ja) * 1982-09-24 1984-04-02 トヨタ自動車株式会社 油圧式バルブリフタ装置
JPS59190412A (ja) * 1983-04-12 1984-10-29 Atsugi Motor Parts Co Ltd 直動型動弁機構
EP0145445B1 (de) * 1983-12-07 1989-03-15 Eaton Corporation Hydraulischer Ventilstössel
DE3409236A1 (de) * 1984-03-14 1985-09-19 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Aeusseres fuehrungsteil fuer einen ventilstoessel
JPS60153801U (ja) * 1984-03-23 1985-10-14 富士バルブ株式会社 内燃機関の油圧式弁間隙調整装置
IT8467294A0 (it) * 1984-03-27 1984-03-27 Riv Officine Di Villar Perosa Punteria idraulica per il comando del moto di una valvola di un motore endotermico
DE3412175A1 (de) * 1984-03-31 1985-10-10 Motomak Motorenbau, Maschinen- u. Werkzeugfabrik, Konstruktionen GmbH, 8070 Ingolstadt Tassenfoermiges gehaeuse eines sich selbsttaetig hydraulisch einstellenden ventilstoessels fuer brennkraftmaschinen mit obenliegender nockenwelle
JPS6155306A (ja) * 1984-08-28 1986-03-19 Riken Corp 油圧タペツトの製造方法
DE3437478A1 (de) * 1984-10-12 1986-04-17 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Sich selbsttaetig hydraulisch einstellender ventilstoessel
JPS61171812A (ja) * 1985-01-28 1986-08-02 Riken Corp 油圧タペツトの製造方法
DE3528432A1 (de) * 1985-08-08 1987-02-19 Motomak Sich selbsttaetig hydraulisch einstellender ventilstoessel
JPH0625607Y2 (ja) * 1985-11-07 1994-07-06 日鍛バルブ株式会社 直動型油圧ラッシュアジャスタ
DE3639911A1 (de) * 1986-11-22 1988-06-01 Schaeffler Waelzlager Kg Sich selbsttaetig hydraulisch einstellender ventilstoessel
DE3828635A1 (de) * 1988-08-24 1990-03-08 Daimler Benz Ag Verfahren zum herstellen von tassenstoesseln fuer hubkolbenmaschinen
JPH0331504A (ja) * 1989-06-27 1991-02-12 Fuji Valve Co Ltd 油圧式バルブラッシュアジャスタ
IT1233099B (it) * 1989-06-28 1992-03-14 Goriziane Off Mec Variatore di fase, particolarmente per la variazione della fase relativa fra l'albero a camme ed il meccanismo di comando della distribuzione in un motore a combustione interna
DE4015719A1 (de) * 1990-05-16 1991-11-21 Gmb Giesserei & Maschinenbau B Uebertragungselement fuer ventilbetaetigungen
DE4444481A1 (de) * 1994-12-14 1996-06-20 Schaeffler Waelzlager Kg Stößel mit einem hydraulischen Ventilspielausgleichselement
DE19617669A1 (de) * 1996-05-03 1997-11-06 Schaeffler Waelzlager Kg Hydraulisches Spielausgleichselement für einen Ventiltrieb einer Brennkraftmaschine
DE19856617A1 (de) * 1998-12-08 2000-06-21 Siemens Ag Element zur Übertragung einer Bewegung und Einspritzventil mit einem solchen Element
DE19858476B4 (de) * 1998-12-17 2006-07-27 Siemens Ag Vorrichtung zum Übertragen einer Aktorauslenkung auf ein Stellglied und Einspritzventil mit einer solchen Vorrichtung
DE102012201914A1 (de) * 2012-02-09 2013-08-14 Schaeffler Technologies AG & Co. KG Transportsicherung mit Zusatzfunktion

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB615341A (en) * 1945-05-03 1949-01-05 Weatherhead Co Improvements in or relating to a tappet
US3509858A (en) * 1968-05-20 1970-05-05 Gen Motors Corp Overhead cam valve lifter
DE1808000A1 (de) * 1968-11-09 1970-05-27 Richard Kuechen Sen Hydraulische,selbsttaetig arbeitende Ventilspielausgleichsvorrichtung
US3658038A (en) * 1971-01-04 1972-04-25 Johnson Products Inc Tappet for overhead camshaft engine
GB2017860B (en) * 1978-03-23 1982-09-29 Aisin Seiki Hydraulic slack adjuster for valve trains of ohc engines
US4227495A (en) * 1978-09-21 1980-10-14 Eaton Corporation Hydraulic lash adjuster with oil reservoir separator
DE2847699C3 (de) * 1978-11-03 1982-03-04 Kamax-Werke Rudolf Kellermann Gmbh & Co Kg, 3360 Osterode Hydraulisches Spielausgleichselement

Also Published As

Publication number Publication date
JPH0120286B2 (de) 1989-04-14
DE3072169D1 (de) 1990-01-18
BR8005733A (pt) 1981-06-09
EP0030781A1 (de) 1981-06-24
JPS5683508A (en) 1981-07-08

Similar Documents

Publication Publication Date Title
EP0030781B1 (de) Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung
US4367701A (en) Acting valve gear
US4590898A (en) Hydraulic tappet for direct-acting valve gear
EP0055399B1 (de) Hydraulisches Ventilspielausgleichelement mit Tauchkolbenhalter
US4470381A (en) Hydraulic tappet for direct-acting valve gear
EP0899429B1 (de) Hydraulisches Ventilspielausgleichselement
EP0145445B1 (de) Hydraulischer Ventilstössel
US5862785A (en) Hydraulic lash adjuster and improved oil flow path therefor
EP0758046A1 (de) Hydraulische Ventilspielausgleichsvorrichtung
US5014599A (en) Two piece hydraulic piston assembly with swaged piston-sleeve joint
US4688526A (en) Self-contained hydraulic bucket lifter
US4462364A (en) Hydraulic lash adjuster
EP2085580B1 (de) Spielausgleichselement
EP0140674A2 (de) Spielausgleichselement mit eingebetteter Verschleissfläche
EP0953734B1 (de) Hydraulisches Spielausgleichselement und Rückschlagventil dafür
US4715334A (en) Self contained hydraulic bucket lifter
JP3268463B2 (ja) 内燃機関用油圧式タペット
US4624224A (en) Hydraulic valve lifter
USRE32167E (en) Acting valve gear
CA2412959A1 (en) Valve spring anti-rotation apparatus
JPH0625526B2 (ja) 油圧式弁間隙自動補正装置
JPS5910329Y2 (ja) 密封式弁間隙自動調整装置
EP0400602B1 (de) Hydraulisches Spielausgleichselement mit direkter Wirkung
JPH0324810Y2 (de)
JPS5913285Y2 (ja) 密封式弁間隙自動調整装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19811116

ITCL It: translation for ep claims filed

Representative=s name: ING. C. GREGORJ S.P.A.

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: EATON CORPORATION

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE IT

ITF It: translation for a ep patent filed

Owner name: ING. C. GREGORJ S.P.A.

REF Corresponds to:

Ref document number: 3072169

Country of ref document: DE

Date of ref document: 19900118

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: GENERAL MOTORS CORPORATION

Effective date: 19900913

Opponent name: PRECISION ENGINE PRODUCTS CORPORATION

Effective date: 19900911

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

R26 Opposition filed (corrected)

Opponent name: PRECISION ENGINE PRODUCTS CORPORATION * 900913 GEN

Effective date: 19900911

ITTA It: last paid annual fee
PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 19941214

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19990831

Year of fee payment: 20

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO