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EP0030781A1 - Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung - Google Patents

Hydraulischer Ventilstössel für eine direkt angetriebene Ventilsteuerung Download PDF

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Publication number
EP0030781A1
EP0030781A1 EP19800302755 EP80302755A EP0030781A1 EP 0030781 A1 EP0030781 A1 EP 0030781A1 EP 19800302755 EP19800302755 EP 19800302755 EP 80302755 A EP80302755 A EP 80302755A EP 0030781 A1 EP0030781 A1 EP 0030781A1
Authority
EP
European Patent Office
Prior art keywords
hub
tappet
plunger
cam
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.)
Granted
Application number
EP19800302755
Other languages
English (en)
French (fr)
Other versions
EP0030781B1 (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
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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

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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

  • 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 resonent 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 speed 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.
  • Known hydraulic tappets for direct-acting valve gear have employed 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, such as that shown and described in U.S. Patent 3,509,858 to Scheibe et al, wherein the necessity of undercutting requires a relatively large plunger guide bore in the body which in turn results in a reduced hydraulic pressure upper operating limit. Furthermore, if the diameter of the plunger guide bore is reduced, the undercut reservoir is reduced in volume and the mass of the tappet is increased, resulting in greater inertia.
  • a further problem encountered in the design of such 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 susceptable 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.
  • the present invention provides an hydraulic lash adjusting tappet of the type used in direct acting valve gear for internal combustion engines operating at high rpm.
  • the hydraulic tappet of the present invention is of the type having a general configuration known as a "bucket" where the body of the tappet has a diameter substantially larger than that of the hydraulic plunger contained therein.
  • 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.
  • the present tappet further employes a unique construction whereby the primary leakdown surfaces from the high pressure chamber are formed between the plunger and a separate piston received therein rather than between the tappet body and the plunger.
  • This construction enables the control of the clearances between the primary leakdown surfaces to be performed on the smaller diameter parts and eliminates the need for machining or grinding precision bore diameters in the tappet body. Scrap losses related to surfaces employed for leakdown control are therefore confined to the plunger piston sub-assembly.
  • the hydraulic tappet of the present invention provides for a relatively small lash adjustment plunger which reduces the load transmitted to the cam and valve at high engine lubricant supply operating pressures.
  • the tappet of the present invention provides for an arrangement wherein the high pressure hydraulic lash adjustment chamber is disposed vertically near or below the lowest level of the hydraulic fluid reservoir to provide the most convenient escape path for any trapped air.
  • the body of the present tappet has a generally tubular outer wall construction with a radially inwardly extending web disposed intermediate the ends with a tubular hub disposed in the center of the body and formed integrally with the web and extending axially therefrom.
  • the face of the tappet is provided by joining a generally disc-shaped member about its periphery to one end of the tubular outer wall portion.
  • the hydraulic plunger and piston assembly is received in the inner hub and the hydraulic reservoir is formed between the inside face of the reverse face of the cam surface member, the outer tubular wall, the web, the inner tubular hub and the plunger.
  • This unique construction provides for a relatively large diameter reservoir of fluid intermediate the hydraulic plunger and inner periphery of the outer wall portion without requiring undercutting of material in forming the tappet body.
  • the resultant assembly of the tappet of the present invention gives a very low profile height for an hydraulic lash adjusting bucket tappet, yet provides relative ease of control in manufacturing of the leakdown surfaces and also yields an adequate reservoir of fluid for the hydraulic lash adjusting mechanism.
  • the tappet of the present invention also provides means for trapped air escape and permits operation at high engine lubricant operating pressures.
  • the tappet of the present invention also provides a unique means for retaining the hydraulic lash adjusting sub-assembly in the body.
  • 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 18 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 portion 42 having a transverse web 44 extending generally radially inwardly from the inner periphery of the outer tubular wall portion at a location intermediate the ends thereof.
  • the web 44 has formed preferably integrally therewith a tubular hub portion 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 portion 42.
  • the outer periphery of the tubular wall portion 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 body portion 42 in a suitable manner, as for example, 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 body portion 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 inner periphery 48 of hub 46 has received therein a plunger 50 having the outer periphery thereof in sliding closely fitting relationship with the interior 48 of the hub.
  • the plunger 50 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 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 lower 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 shoulder 54 such that the retainer 56 serves to limit the downward motion of the plunger 49.
  • the plunger 50 has a precision cylindrical bore 62 formed in the upper end thereof with the lower end thereof terminating in a shouldered flat bottom 64.
  • the precision bore 62 has slidably received therein in very closely fitting relationship a piston member 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 seating surface 74.
  • a one-way valve member in the form of check-ball 72 rests against the annular seating surface 74, and is, as known in the art and described in the copending application of John J. Krieg, Serial No. , filed , and assigned to the assignee of the present invention, biased thereagainst by a suitable expedient as, for example, a conical check-ball spring 76.
  • the check-ball 72 is retained by the cage 78 which has an outwardly extending flange 80 received in counterbore 70 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 and as described in the aforesaid patent application of J. Krieg.
  • 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 64 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 fluid reservoir which is communicated with the region externally of the body periphery 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 the second portion 85 of the reservoir bounded by piston bore 70 and the underface of member 18 in continuous fluid communication with the outer regions 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 chambers 86.
  • the fluid retained in the second portion 85 of the fluid reservoir supplies the one-way valve 72 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 region 86 below the piston check-ball and seat 74 and bounded by the bore of the plunger the bottom 64 of the plunger comprises a high pressure fluid chamber for retaining therein fluid entering through passage 68 upon opening of the check-ball 72.
  • valve 72 is biased in 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 18 of the tappet.
  • the cam load contacts the upper face 18 of the tappet, causing the tappet to move downwardly to the position indicated in dashed outline 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 64 which draws open the check-ball 72 to the position shown in Fig. 4 permitting fluid to flow into chamber 86. Upon cessation of the expansion of chamber 86, the check-ball 72 closes under the biasing spring 76.
  • the ramp of the cam lobe begins to exert a downward force on the upper face 18 of the tappet tending to compress the piston 64 into bore 62 in the plunger, which compression is resisted by fluid trapped in chamber 86.
  • the fluid trapped in the chamber 86 prevents substantial movement of the piston 64 relative to plunger 50 and transmits the motion through the bottom face of plunger 52 onto the top of the valve stem 26. It will be understood by those having ordinary skill in the art that a minor movement of the plunger with respect to the piston occurs, the magnitude of which is controlled by the amount of fluid permitted to pass through the aforesaid leakdown surfaces 62 and 66.
  • the piston 64 and plunger 50 thus act as a rigid member transmitting further lifts of cam lobe 16 for opening the valve to the position shown by dashed line in Fig. 1.
  • 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 portion 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 means 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 108, 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 108 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 35mm.
  • 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 portion 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.
  • FIG. 7 an alternate embodiment of the tappet 10 is illustrated having a body outer tubular wall portion 140 closed at the upper end thereof by transverse web 142 having the upper surface thereof hardened for contacting a cam.
  • the web 142 is preferably formed integrally with the outer wall 140 and of a suitable iron base material such as a readily formable and hardenable steel.
  • the outer wall 140 has a preferably annular rib 144 extending from the inner surface thereof intermediate the ends of the outer wall portion and has a circumferential groove 146 formed in the inner periphery of the wall portion 140 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 wall 140 with the upper surface of annular member 146 registering against the lower surface of annular rib 144.
  • the annular member 146 has a downwardly extending annular hub portion 148 formed integrally therewith and centrally disposed with respect thereto which hub portion 148 has received therein a suitable hydraulic lash-adjusting assembly indicated generally at 150 and which is 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 the lip 152.
  • the outer periphery of annular member 146 has an annular wall portion 154 extending downwardly with respect to Figure 7 from the outer periphery of the annular member 146 and along the inner surface of the wall portion 141 of the tappet body.
  • the lower edge of wall 154 is deformed outwardly into the groove 146 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 provides the outer annular 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 mechanism 150 in tappet 140 is otherwise identical to that described hereinabove with respect to the embodiments of Figures 2 thru 5.
  • the embodiment of Figure 7 provides a simplified structure for the bucket or tappet body; however, a separate insert member is required to provide for the outer portion of the fluid reservoir and the supporting hub for the lash-adjusting mechanism.
  • FIG. 8 another embodiment of the tappet is denoted generally at 160 which employs the body having an outer tubular wall portion 162 with a transverse web 164 closing the upper end therefor with respect to Figure 8 and providing on the upper surface of the web 164, a suitably hardenable surface for contacting a cam.
  • the outer wall 162 and web 164 are formed of a suitably hardenable iron base material as, for example, a high carbon steel.
  • An inner tubular hub 166 is joined with the undersurface of web 164 and extends downwardly therefrom in Figure 8 and is disposed generally centrally with respect thereto.
  • the inner periphery of the hub 166 is has received therein an hydraulic lash adjusting sub-assembly 150 in the same manner and function as in the embodiment described above with respect to Figure 7.
  • an annular member 168 is received in contact with the inner periphery of the outer wall 162 and registers against an annular rib 168 formed on the inner periphery of wall 162.
  • Annular member 168 has upper surface thereof in the region adjacent the inner periphery registering against the end of hub 166 with an annular wall portion 170 extending upwardly over the outer periphery of the hub 166.
  • a seal member 172 is received in a groove provided in the outer periphery of hub 166, which seal member provides a seal between the hub and inner periphery of annular wall 170.
  • the annular member, including wall 170 is formed of a light-weight relatively soft material as, for example, aluminum, which is retained in the inner periphery of the body by suitably staking the outer periphery of the member 168 radially outwardly in the rim portion 174 provided about the outer periphery thereof.
  • the embodiment of Figure 8 thus provides a tubular hub formed integrally with the web and outer wall to provide relatively hard sliding surfaces for the inner periphery of the hub to which the lash adjuster 150 is received.
  • the embodiment of Figure 8 enables the use of an annular member formed of soft material such as aluminum for closing the outer annular portion 176 of the fluid reservoir.
  • the embodiment of Figure 8 is otherwise functionally similar to the embodiments of Figures 2 thru 7.
  • 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 employs a hardened steel disc attached over one end of a tubular body for providing the cam face of the tappet.
  • the tubular body has formed integrally therewith an inwardly extending web disposed intermediate the ends of the tubular wall, with the web having formed integrally therewith a centrally disposed tubular hub for receiving the hydraulic lash adjusting plunger mechanism.
  • the plunger mechanism is retained preferably by retaining means engaging the wall of the tubular hub or alternatively, by snap ring provided in the outer periphery of the plunger.
  • the novel construction of the present 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 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 reservoir for fluid to supply the one-way check valve for the hydraulic lash adjusting means.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
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 true EP0030781A1 (de) 1981-06-24
EP0030781B1 EP0030781B1 (de) 1989-12-13

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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

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

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0055399A1 (de) * 1980-12-29 1982-07-07 Eaton Corporation Hydraulisches Ventilspielausgleichelement mit Tauchkolbenhalter
EP0085373A1 (de) * 1982-02-02 1983-08-10 INA Wälzlager Schaeffler KG Verfahren zum flüssigkeitsdichten Befestigen des äusseren Randes eines flanschartigen Blechteiles in der Bohrung eines Ventilstössels und Vorrichtung zur Durchführung des Verfahrens
EP0145445A2 (de) * 1983-12-07 1985-06-19 Eaton Corporation Hydraulischer Ventilstössel
DE3409236A1 (de) * 1984-03-14 1985-09-19 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Aeusseres fuehrungsteil fuer einen ventilstoessel
FR2562157A1 (fr) * 1984-03-31 1985-10-04 Motomak Capot en forme de cuvette pour poussoir de soupape a reglage hydraulique automatique, pour moteurs a combustion interne a arbre a cames en tete
EP0179323A1 (de) * 1984-10-12 1986-04-30 INA Wälzlager Schaeffler KG Sich selbsttätig hydraulisch einstellender Ventilstössel
US4610225A (en) * 1984-03-27 1986-09-09 Riv-Skf Officine Di Villar Perosa, Spa Hydraulic tappet for controlling an internal combustion engine valve
EP0212162A1 (de) * 1985-08-08 1987-03-04 MOTOMAK Motorenbau, Maschinen- und Werkzeugfabrik, Konstruktionen GmbH Sich selbsttätig hydraulisch einstellender Ventilstössel
EP0090105B1 (de) * 1982-03-29 1989-12-20 Alfred Anthony Black Verstellbarer Ventilfederteller für eine Brennkraftmaschine
EP0272423B1 (de) * 1986-11-22 1991-04-10 INA Wälzlager Schaeffler KG Sich selbsttätig hydraulisch einstellender Ventilstössel
DE4015719A1 (de) * 1990-05-16 1991-11-21 Gmb Giesserei & Maschinenbau B Uebertragungselement fuer ventilbetaetigungen
EP0405383B1 (de) * 1989-06-28 1995-10-18 Carraro S.P.A. Einrichtung zur Veränderung der Steuerzeiten, insbesondere zur Verstellung der Phasenanlage zwischen der Nockenwelle und deren Antrieb in Brennkraftmaschinen
WO1996018806A1 (de) * 1994-12-14 1996-06-20 Ina Wälzlager Schaeffler Kg Stössel mit einem hydraulischen ventilspielausgleichselement
WO1997042401A1 (de) * 1996-05-03 1997-11-13 INA Wälzlager Schaeffler oHG Hydraulisches spielausgleichselement für einen ventiltrieb einer brennkraftmaschine
WO2000034645A1 (de) * 1998-12-08 2000-06-15 Siemens Aktiengesellschaft Element zur übertragung einer bewegung und einspritzventil mit einem solchen element
WO2000036293A1 (de) * 1998-12-17 2000-06-22 Siemens Aktiengesellschaft Vorrichtung zum übertragen einer aktorauslenkung auf ein stellglied und einspritzventil mit einer solchen vorrichtung
WO2013117374A1 (de) * 2012-02-09 2013-08-15 Schaeffler Technologies AG & Co. KG Transportsicherung mit zusatzfunktion

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
JPS6155306A (ja) * 1984-08-28 1986-03-19 Riken Corp 油圧タペツトの製造方法
JPS61171812A (ja) * 1985-01-28 1986-08-02 Riken Corp 油圧タペツトの製造方法
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
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

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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
GB2017860A (en) * 1978-03-23 1979-10-10 Aisin Seiki Hydraulic slack adjuster for valve trains of ohc engines
GB2032039A (en) * 1978-09-21 1980-04-30 Eaton Corp Hydraulic tappet with oil reservoir
EP0010768A1 (de) * 1978-11-03 1980-05-14 Kamax-Werke Rudolf Kellermann GmbH & Co. KG Hydraulisches Spielausgleichselement

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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
GB2017860A (en) * 1978-03-23 1979-10-10 Aisin Seiki Hydraulic slack adjuster for valve trains of ohc engines
GB2032039A (en) * 1978-09-21 1980-04-30 Eaton Corp Hydraulic tappet with oil reservoir
EP0010768A1 (de) * 1978-11-03 1980-05-14 Kamax-Werke Rudolf Kellermann GmbH & Co. KG Hydraulisches Spielausgleichselement

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0055399A1 (de) * 1980-12-29 1982-07-07 Eaton Corporation Hydraulisches Ventilspielausgleichelement mit Tauchkolbenhalter
EP0085373A1 (de) * 1982-02-02 1983-08-10 INA Wälzlager Schaeffler KG Verfahren zum flüssigkeitsdichten Befestigen des äusseren Randes eines flanschartigen Blechteiles in der Bohrung eines Ventilstössels und Vorrichtung zur Durchführung des Verfahrens
EP0090105B1 (de) * 1982-03-29 1989-12-20 Alfred Anthony Black Verstellbarer Ventilfederteller für eine Brennkraftmaschine
EP0145445A2 (de) * 1983-12-07 1985-06-19 Eaton Corporation Hydraulischer Ventilstössel
EP0145445A3 (en) * 1983-12-07 1986-02-26 Eaton Corporation Self-contained hydraulic bucket lifter
DE3409236A1 (de) * 1984-03-14 1985-09-19 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Aeusseres fuehrungsteil fuer einen ventilstoessel
US4610225A (en) * 1984-03-27 1986-09-09 Riv-Skf Officine Di Villar Perosa, Spa Hydraulic tappet for controlling an internal combustion engine valve
FR2562157A1 (fr) * 1984-03-31 1985-10-04 Motomak Capot en forme de cuvette pour poussoir de soupape a reglage hydraulique automatique, pour moteurs a combustion interne a arbre a cames en tete
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
EP0179323A1 (de) * 1984-10-12 1986-04-30 INA Wälzlager Schaeffler KG Sich selbsttätig hydraulisch einstellender Ventilstössel
US4745889A (en) * 1985-08-08 1988-05-24 Motomak Motorenbau, Maschinen-Und Werkzeugfabrik, Konstruktionen Gmbh Hydraulic valve tappet
EP0212162A1 (de) * 1985-08-08 1987-03-04 MOTOMAK Motorenbau, Maschinen- und Werkzeugfabrik, Konstruktionen GmbH Sich selbsttätig hydraulisch einstellender Ventilstössel
EP0272423B1 (de) * 1986-11-22 1991-04-10 INA Wälzlager Schaeffler KG Sich selbsttätig hydraulisch einstellender Ventilstössel
EP0405383B1 (de) * 1989-06-28 1995-10-18 Carraro S.P.A. Einrichtung zur Veränderung der Steuerzeiten, insbesondere zur Verstellung der Phasenanlage zwischen der Nockenwelle und deren Antrieb in Brennkraftmaschinen
DE4015719A1 (de) * 1990-05-16 1991-11-21 Gmb Giesserei & Maschinenbau B Uebertragungselement fuer ventilbetaetigungen
WO1996018806A1 (de) * 1994-12-14 1996-06-20 Ina Wälzlager Schaeffler Kg Stössel mit einem hydraulischen ventilspielausgleichselement
US5727509A (en) * 1994-12-14 1998-03-17 Ina Walzlager Schaeffler Kg Cam follower in the form of a tappet or a lever having a hydraulic valve clearance compensation element
US5890463A (en) * 1994-12-14 1999-04-06 Ina Walzlager Schaeffler Kg Tappet with a hydraulic valve clearance compensation element
WO1997042401A1 (de) * 1996-05-03 1997-11-13 INA Wälzlager Schaeffler oHG Hydraulisches spielausgleichselement für einen ventiltrieb einer brennkraftmaschine
DE19681469B4 (de) * 1996-05-03 2006-04-27 Ina-Schaeffler Kg Hydraulisches Spielausgleichselement für einen Ventiltrieb einer Brennkraftmaschine
WO2000034645A1 (de) * 1998-12-08 2000-06-15 Siemens Aktiengesellschaft Element zur übertragung einer bewegung und einspritzventil mit einem solchen element
WO2000036293A1 (de) * 1998-12-17 2000-06-22 Siemens Aktiengesellschaft Vorrichtung zum übertragen einer aktorauslenkung auf ein stellglied und einspritzventil mit einer solchen vorrichtung
WO2013117374A1 (de) * 2012-02-09 2013-08-15 Schaeffler Technologies AG & Co. KG Transportsicherung mit zusatzfunktion

Also Published As

Publication number Publication date
JPH0120286B2 (de) 1989-04-14
EP0030781B1 (de) 1989-12-13
BR8005733A (pt) 1981-06-09
JPS5683508A (en) 1981-07-08
DE3072169D1 (de) 1990-01-18

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