EP1591629A1 - Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements - Google Patents
Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements Download PDFInfo
- Publication number
- EP1591629A1 EP1591629A1 EP04101692A EP04101692A EP1591629A1 EP 1591629 A1 EP1591629 A1 EP 1591629A1 EP 04101692 A EP04101692 A EP 04101692A EP 04101692 A EP04101692 A EP 04101692A EP 1591629 A1 EP1591629 A1 EP 1591629A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- groove
- longitudinal axis
- plunger
- rotation
- 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
Links
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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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/16—Silencing impact; Reducing wear
-
- 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
- F01L1/02—Valve drive
- F01L1/022—Chain drive
-
- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead camshafts
-
- 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
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/01—Absolute values
Definitions
- the invention relates to a system comprising a cam with a cam nose and a cam follower, which upon rotation of the cam a oscillating stroke movement in the direction of its longitudinal axis, either the center plane of the cam, which is perpendicular to the axis of rotation of the cam, relative to the longitudinal axis of the cam follower element by an eccentricity E1 is arranged offset, or on the one hand, a contact surface of the follower element Crown and on the other hand the cam has a cam bevel with regard to it Having an axis of rotation, so that the cam follower element rotates about its longitudinal axis, when the cam extends with its cam surface along a contact line engaged with the cam follower.
- the invention relates to the use of such a system.
- a system of the type mentioned above for example, in an internal combustion engine used a motor vehicle.
- a four-stroke working method comprises in addition to the compression of the fuel air mixture or the combustion air and the expansion due to the combustion taking place in the combustion chamber and the Charge exchange.
- To control the Charge changes in four-stroke engines are almost exclusively globe valves used, which oscillates during operation of the internal combustion engine Execute lifting movement and in this way the opening and closing operation perform the inlet and outlet openings.
- Valve gear designates. It is the task of the valve train, the intake and To release exhaust ports of the combustion chamber in time or close, where a quick release of the largest possible flow cross-sections is sought to to keep the throttling losses in the inflowing and outflowing gas flows low and the best possible filling of the combustion chamber with fresh mixture or a effective i. ensure complete expulsion of the combustion gases.
- a valve is used for this purpose in the rule along its longitudinal axis between a valve closing position and a Valve open position is movable to an inlet or outlet opening of a Release combustion chamber of the internal combustion engine or block.
- valve springs are provided to the Prevent valve in the direction of valve closing position, and on the other Valve actuator used to the valve against the biasing force to open the valve spring means.
- the valve actuating device comprises a camshaft on which a plurality of Cam is arranged and - for example by means of a chain drive - of the crankshaft is rotated in the manner that the camshaft and with this orbits the cam at half the crankshaft speed.
- Bottom camshafts are suitable for the actuation of so-called standing valves, but also with the help of bumpers and levers, For example, swing levers or rocker arms, hanging for the operation Valves.
- Standing valves are opened by moving them upwards, whereas hanging valves are opened by a downward movement.
- a plunger is used as an intermediate element, at least during the opening and closing operation with the cam of the camshaft in Engaged.
- overhead camshafts are exclusively for actuation used overhead valves, wherein a valve train with overhead camshaft as another valve drive component a rocker arm, a rocker arm or a Tappet has.
- the rocker arm rotates about a fixed pivot point and When displaced by the cam, the valve moves against the preload force the valve spring means towards the valve open position.
- the cam engages the an end of the rocker arm, wherein the valve at the opposite end of the Levers is arranged.
- this plunger When using a plunger, this plunger is on the combustion chamber remote end of the lift valve placed so that the plunger on the oscillating stroke movement of the valve participates when the cam is with his Cam surface in the area of the cam nose along a contact line in Intervention is with the plunger.
- An advantage of using overhead camshafts is that in particular by the omission of the bumper the moving mass of Valve gear is reduced and the valve gear rigid i. less elastic.
- This lubricating oil film is comparable to the structure of the lubricating oil layer in one Plain bearing, in the present case the number of lubricants, which is a measure of the Carrying capacity of the lubricating oil film does not represent the difference of the relative Component speeds depends, but on the sum of the relative Component speeds.
- the wear of the cam and pestle is not only disadvantageous in terms of the Life of these components, but also in particular in terms of Functioning of the valve train.
- a material removal on the Cam surface and / or the plunger surface has in fact an influence on the valve clearance and on the other effects on the valve lift and the Control times i. on the crank angle to which the valve is opened and is closed.
- Another measure to counteract the wear of plunger and cam is to arrange the cam and the plunger to each other in such a way that the center plane of the cam, which is perpendicular to the axis of rotation of the cam, with respect to the longitudinal axis of the plunger around a Eccentricity E 1 is arranged offset. This eccentricity causes the plunger to rotate about its longitudinal axis when the cam is engaged with its cam surface along a line of contact with the plunger.
- the rotation of the plunger is caused by the left and right of The ram longitudinal axis located portions of the cam surface differently are big.
- the differently sized cam areas act on the plunger - predominantly - with different sized torques, which is why the plunger is set in rotation due to the difference of these two torques.
- the Torques result from the product of the pressure point radius, which turns out to be Distance between the respective cam area center of the longitudinal axis of the plunger represents, and the average frictional force resulting from the pressures and the Friction coefficient along the line of contact of the cam portion in the The result is that the average friction force with the pressure point radius as a lever to an equal torque around the longitudinal axis of the plunger leads like the actually occurring along the line of contact with their frictional forces respective levers.
- the local pressure along the contact line and thus the local Lubricating number i. the carrying capacity in which between cam surface and Tappet surface forming lubricating oil film - as already mentioned above - from the Sum of the individual relative component speeds dependent, the one to specific time varies locally. Because the component speed of the plunger varies along the contact line d. H. it increases with the peripheral speed increasing radius due to the rotational movement.
- a decreasing lubricating has basically the disadvantage that with the decreasing bearing capacity of the lubricating film initially increasing the area of Fluid friction is left and a transition to mixed friction takes place, with always decreasing lubricity, the proportion of solid friction always increases more.
- the cam surface of the cam a Has in the direction of rotation locally varying radius of curvature, so that the Speed at which the cam slides over the plunger surface, at least changes in the area of the cam nose with the cam rotation angle. Also this effect leads to constantly changing conditions in the lubricating film along the Contact line. Those responsible for the carrying capacity of the lubricating film Parameters change once locally along the contact line and also in Dependence on time
- the object of the present invention is a system of the generic type, with those of the prior art known disadvantages are overcome, and in particular a lower Wear has.
- Another object of the present invention is to provide uses of show such system.
- the first sub-task is solved by a system comprising a cam with a cam lobe and a cam follower, which performs an oscillating lifting movement in the direction of its longitudinal axis with a rotation of the cam, wherein either the center plane of the cam, which is perpendicular to the axis of rotation of the cam, with respect to the
- the longitudinal axis of the cam follower element is arranged offset by an eccentricity E 1 , or on the one hand a contact surface of the follower crown and on the other hand, the cam has a cam bevel with respect to its axis of rotation, so that the cam follower element rotates about its longitudinal axis when the cam along with its cam surface along a contact line is in engagement with the cam follower element, and which is characterized in that the cam has at least in the circumferential direction at least in the region of the cam lobe in its cam surface.
- the inventive construction of the cam with at least one groove in Circumferential direction is the result of wear tests by means of Radionuclide technology RTM performed on a valve train.
- valve train As a tribological system, the valve train has become one of the most wear-intensive Systems of an internal combustion engine selected. To the wear of this system In addition, measures were being considered to promote the training of Lubricating oil film between the cam surface and plunger surface difficult and obstruct. These considerations eventually led to the arrangement of a groove in the cam surface of the cam.
- this groove was a suitable tool for the Lubricating oil film between plunger and cam or the formation of the lubricating oil film and thus to adversely affect the carrying capacity of the lubricating oil film.
- This The assumption was based on the consideration that due to the groove no viable Lubricating oil film could train at least in the region of the groove, as this necessary pressure build-up in the lubricating oil film could not be achieved.
- a Reduction of the carrying capacity of the lubricating oil film should reduce the proportion of Solid friction along the contact line between plunger and cam increase, which has been effective in view of the desired increase in wear would.
- the first object of the invention is achieved, namely a To provide system of the generic type with which the state of the Technology known disadvantages overcome, and in particular one has lower wear.
- pittings are micro-fatigue fractures, the u. a. caused by acting between the cam and plunger Force is not perpendicular to the cam surface, but because of their Friction force component acts more or less obliquely on the cam surface.
- Friction force component acts more or less obliquely on the cam surface.
- Cam follower is a plunger or a washer which the Moves stroke movement to another transmission element.
- Embodiments of the system have proved to be advantageous in which
- the at least one groove has a width S with S ⁇ 0.5 NB, where NB is the width of the cam in the direction designated its longitudinal axis.
- S ⁇ 0.35 are particularly advantageous NB, preferably S ⁇ 0.25 NB.
- the at least one groove has a width S with S ⁇ 0.75 mm.
- This embodiment contributes to the fact that the groove has a certain minimum width In order to ensure the formation of a viable lubricating oil film in the range of at least to safely prevent a groove.
- embodiments of the system are advantageous which have at least one groove over the entire circumference of the Cam shell surface extending annular groove.
- valve gears where the cam not only in the area of the cam nose, but also in the cam nose region of the cam, i. in the area of Base circle of the cam is engaged with the plunger, this is closed annular formation of the at least one groove advantageous to over the entire Scope to realize a reduction in wear.
- the at least one groove has a depth D with D ⁇ 0.8 mm.
- This embodiment contributes - similar to the requirement for a minimum width S min of the at least one groove - the fact that the groove must also have a certain minimum depth to safely prevent the formation of a viable lubricating oil film in the region of at least one groove.
- the second of the invention underlying subtask is achieved in that the system is used in a valve train of a piston working machine.
- FIG. 1 schematically shows a first embodiment of the system 1 in one embodiment Side view in a viewing direction perpendicular to the axis of rotation 4 of the Camshaft 9 and perpendicular to the longitudinal axis 12 of the plunger 11 is.
- the system 1 comprises a cam 2 with a cam nose 3 and a plunger 11.
- the cam 2 is arranged on a camshaft 9 and rotates with this Camshaft 9 about its longitudinal axis. 4
- the cam 2 and the plunger 11 are arranged to each other in such a way that the center plane 5 of the cam 2, which is perpendicular to the axis of rotation 4 of the cam 2, with respect to the longitudinal axis 12 of the plunger 11 is arranged offset by an eccentricity E 1 , so that the plunger 11 rotates about its longitudinal axis 12 when the cam 2 engages with its cam surface 6 along a line of contact 10 with the plunger 11.
- the cam 2 rotates about its Longitudinal axis 4, while the plunger 11 due to the deflection by the cam second performs an oscillating lifting movement in the direction of its longitudinal axis 12.
- a coupled to the plunger 11 valve is characterized along its longitudinal axis between a valve closed position and a valve open position moves and gives while an inlet or outlet opening of a combustion chamber of the internal combustion engine free or blocked this.
- the plunger 11 moves in deflection by the cam 2 the valve against the biasing force of the valve spring means in the direction Valve open position, wherein the valve by the valve spring means, which the valve in Direction to close valve closing position, is closed again.
- the cam 2 is characterized in that it has in the circumferential direction a groove 7 in its cam surface 6, wherein the center line 8 of the groove 7 is arranged offset from the center plane 5 of the cam 2 by an eccentricity E 2 .
- the eccentricity E 2 2.5mm
- S 0.14 NB.
- the groove 7 divides the cam 2 into two areas.
- the different sized cam areas act on the plunger 11 with different sized torques.
- the torques result from the product of the respective pressure point radius R 1 , R 2 and the respective average friction force F 1 , F 2 , which results from the pressures along the contact line 10 of the respective cam portion in such a way that the average friction force F 1 , F 2 with the pressure point radius R 1 , R 2 as a lever to an equal torque around the longitudinal axis 12 of the plunger 11 as the actually occurring along the contact line 10 pressures or forces with their respective levers.
- cam 2 is provided with a groove 7, the wear of Tappet 11 and cam 2 compared to the prior art significantly lowered.
- Figure 2 shows schematically a second embodiment of the system 1 in one Side view.
- the eccentricity E 1 by which the center plane 5 of the cam 2 is arranged offset with respect to the longitudinal axis 12 of the plunger 11, corresponds in magnitude to the eccentricity E 2 , about which the center line 8 of the groove 7 is offset relative to the center plane 5 of the cam 2, wherein the eccentricity E 1 is positive, ie, directed to the left, whereas the eccentricity E 1 is directed negative, ie to the right.
- the center line 8 of the groove 7 is aligned with the longitudinal axis 12 of the plunger eleventh
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
NB | E 1 | E 2 | S | D | B 1 | B 2 | R 1 | R 2 | |
Beispiel 1 | 14 | 1,5 | 2,5 | 2 | 0,8 | 8,5 | 3,5 | 1,25 | 6,75 |
Beispiel 2 | 14 | 1 | -1 | 3 | 1 | 4,5 | 6,5 | 3,75 | 4,75 |
- Fig.1
- schematisch eine erste Ausführungsform des Systems in einer Seitenansicht, und
- Fig. 2
- schematisch eine zweite Ausführungsform des Systems in einer Seitenansicht.
- 1
- System
- 2
- Nocken
- 3
- Nockennase
- 4
- Längsachse, Drehachse des Nockens
- 5
- Mittelebene des Nockens
- 6
- Nockenmantelfläche
- 7
- Nut
- 8
- Mittellinie der Nut
- 9
- Nockenwelle
- 10
- Berührungslinie zwischen Nocken und Element
- 11
- Nockenfolgeelement, Element, Stößel
- 12
- Längsachse des Elementes
- α
- Winkel zwischen der Mittellinie der Nut und der Längsachse des Nockens
- B1
- Breite des links von der Nut liegenden Nockenbereiches
- B2
- Breite des rechts von der Nut liegenden Nockenbereiches
- D
- Tiefe der Nut
- E1
- Exzentrizität der Mittelebene des Nockens gegenüber der Längsachse des Elementes
- E2
- Exzentrizität der Mittellinie der Nut gegenüber der Mittelebene des Nockens
- F1
- mittlere Reibungskraft
- F2
- mittlere Reibungskraft
- NB
- Breite des Nockens in Richtung seiner Längsachse
- R1
- Radius des linken Druckpunktes von der Längsachse des Elementes
- R2
- Radius des rechten Druckpunktes von der Längsachse des Elementes
- S
- Breite der Nut
- Smin
- Mindestbreite
Claims (23)
- System (1) umfassend einen Nocken (2) mit einer Nockennase (3) und ein Nockenfolgeelement (11), welches bei einer Rotation der Nocke (2) eine oszillierende Hubbewegung in Richtung seiner Längsachse (12) vollzieht, wobeientweder die Mittelebene (5) des Nockens (2), die senkrecht zur Drehachse (4) des Nockens (2) verläuft, gegenüber der Längsachse (12) des Nockenfolgeelementes (11) um eine Exzentrizität E1 versetzt angeordnet ist,oder zum einen eine Berührfläche des Folgeelementes (11) eine Balligkeit und zum anderen der Nocken (2) eine Nockenschräge hinsichtlich seiner Drehachse (4) aufweist,so daß das Nockenfolgeelement (11) um seine Längsachse (12) rotiert, wenn der Nocken (2) sich mit seiner Nockenmantelfläche (6) entlang einer Berührungslinie (10) in Eingriff befindet mit dem Nockenfolgeelement (11),der Nocken (2) in Umfangsrichtung zumindest im Bereich der Nockennase (3) mindestens eine Nut (7) in seiner Nockenmantelfläche (6) aufweist.
- System (1) nach Anspruch 1,
dadurch gekennzeichnet, daß
das Nockenfolgeelement (11) ein Stößel (11) ist. - System (1) nach Anspruch 1,
dadurch gekennzeichnet, daß
das Nockenfolgeelement (11) eine Unterlegscheibe ist. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
|E1| ≤ 0,5 NB ist, wobei NB die Breite des Nockens (2) in Richtung seiner Längsachse (4) bezeichnet. - System (1) nach Anspruch 4,
dadurch gekennzeichnet, daß
|E1| ≤ 0,35 NB ist. - System (1) nach Anspruch 4 oder 5,
dadurch gekennzeichnet, daß
|E1|≤ 0,25 NB ist. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
die Mittellinie (8) der mindestens einen Nut (7) mit der Längsachse (4) des Nockens (2) einen rechten Winkel α = 90° bildet d.h. parallel zur Mittelebene (5) des Nockens (2) verläuft. - System (1) nach Anspruch 7,
dadurch gekennzeichnet, daß
die Mittellinie (8) der mindestens einen Nut (7) in der Mittelebene (5) des Nockens (2) liegt. - System (1) nach Anspruch 7,
dadurch gekennzeichnet, daß
die Mittellinie (8) der mindestens einen Nut (7) gegenüber der Mittelebene (5) des Nockens (2) um eine Exzentrizität E2 versetzt angeordnet ist. - System (1) nach Anspruch 9,
dadurch gekennzeichnet, daß
|E2| ≤ 0,45 NB ist, wobei NB die Breite des Nockens (2) in Richtung seiner Längsachse (4) bezeichnet. - System (1) nach Anspruch 10,
dadurch gekennzeichnet, daß
|E2| ≤ 0,35 NB ist. - System (1) nach Anspruch 10 oder 11,
dadurch gekennzeichnet, daß
|E2| ≤ 0,25 NB ist. - System (1) nach einem der Ansprüche 10 bis 12,
dadurch gekennzeichnet, daß
|E2| ≤ 0,15 NB ist. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
E1 = - E2 gilt, so daß die Mittellinie (8) der mindestens einen Nut (7) mit der Längsachse (12) des Nockenfolgeelements (11) fluchtet. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
die mindestens eine Nut (7) eine Breite S aufweist mit S ≤ 0,5 NB, wobei NB die Breite des Nockens (2) in Richtung seiner Längsachse (4) bezeichnet. - System (1) nach Anspruch 15,
dadurch gekennzeichnet, daß
S ≤ 0,35 NB ist. - System (1) nach Anspruch 15 oder 16,
dadurch gekennzeichnet, daß
S ≤ 0,25 NB ist. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
die mindestens eine Nut (7) eine Breite S aufweist mit S ≥ 0,75mm. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
die mindestens eine Nut (7) eine über den gesamten Umfang der Nockenmantelfläche (6) verlaufende ringförmige Nut (7) ist. - System (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
die mindestens eine Nut (7) eine Tiefe D aufweist mit D ≥ 0,8mm. - Verwendung eines Systems (1) nach einem der vorherigen Ansprüche,
dadurch gekennzeichnet, daß
das System (1) in einem Ventiltrieb einer Kolbenarbeitsmaschine verwendet wird. - Verwendung eines Systems (1) nach einem der Ansprüche 1 bis 20,
dadurch gekennzeichnet, daß
das System (1) in einem Ventiltrieb einer Verbrennungskraftmaschine verwendet wird. - Verwendung eines Systems (1) nach einem der Ansprüche 1 bis 20,
dadurch gekennzeichnet, daß
das System (1) als Einspritzpumpenbetätigung verwendet wird.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04101692A EP1591629B1 (de) | 2004-04-23 | 2004-04-23 | Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements |
DE502004003276T DE502004003276D1 (de) | 2004-04-23 | 2004-04-23 | Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements |
US11/106,266 US7219638B2 (en) | 2004-04-23 | 2005-04-14 | System comprising a cam and a cam follower element and use of such a system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04101692A EP1591629B1 (de) | 2004-04-23 | 2004-04-23 | Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1591629A1 true EP1591629A1 (de) | 2005-11-02 |
EP1591629B1 EP1591629B1 (de) | 2007-03-21 |
Family
ID=34928997
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04101692A Expired - Lifetime EP1591629B1 (de) | 2004-04-23 | 2004-04-23 | Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements |
Country Status (3)
Country | Link |
---|---|
US (1) | US7219638B2 (de) |
EP (1) | EP1591629B1 (de) |
DE (1) | DE502004003276D1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012204621A1 (de) * | 2012-03-22 | 2013-09-26 | Schaeffler Technologies AG & Co. KG | Nockenstück für einen variablen Schiebenockenventiltrieb |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB323326A (en) * | 1928-11-22 | 1930-01-02 | White & Poppe Ltd | Cam mechanism |
GB513805A (en) * | 1938-05-25 | 1939-10-23 | Charles Lidiard Jenner | Valve gear for internal combustion engines |
US3301239A (en) * | 1963-07-13 | 1967-01-31 | Thauer Peter | Adjustable valve drive for internal combustion engines |
GB1171729A (en) * | 1968-06-14 | 1969-11-26 | Ford Motor Co | Internal combustion engine. |
DE3935154A1 (de) * | 1989-10-21 | 1990-10-31 | Daimler Benz Ag | Auf der gleitflaeche eines betaetigungsgliedes fuer ein gaswechselventil einer hubkolbenmaschine ablaufender steuernocken |
DE19501062A1 (de) * | 1994-02-28 | 1995-08-31 | Schaeffler Waelzlager Kg | Stößel für einen Ventiltrieb einer Brennkraftmaschine |
US5860398A (en) * | 1997-10-28 | 1999-01-19 | Koerner; Jeffrey Scott | Engine tappet |
DE19902446A1 (de) * | 1999-01-22 | 2000-07-27 | Schaeffler Waelzlager Ohg | Ventiltrieb einer Brennkraftmaschine |
US20010027766A1 (en) * | 1996-12-20 | 2001-10-11 | Walter Speil | Tappet for a valve mechanism of an internal combustion engine |
US6435150B1 (en) * | 2000-07-25 | 2002-08-20 | Daimlerchrysler Corporation | Offset tappet assembly |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1541069A (en) * | 1923-01-16 | 1925-06-09 | Galen H Peters | Four-cycle internal-combustion engine |
US2843095A (en) * | 1956-03-05 | 1958-07-15 | Leon A Prentice | Three dimensional cam mechanism |
-
2004
- 2004-04-23 DE DE502004003276T patent/DE502004003276D1/de not_active Expired - Lifetime
- 2004-04-23 EP EP04101692A patent/EP1591629B1/de not_active Expired - Lifetime
-
2005
- 2005-04-14 US US11/106,266 patent/US7219638B2/en not_active Expired - Fee Related
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB323326A (en) * | 1928-11-22 | 1930-01-02 | White & Poppe Ltd | Cam mechanism |
GB513805A (en) * | 1938-05-25 | 1939-10-23 | Charles Lidiard Jenner | Valve gear for internal combustion engines |
US3301239A (en) * | 1963-07-13 | 1967-01-31 | Thauer Peter | Adjustable valve drive for internal combustion engines |
GB1171729A (en) * | 1968-06-14 | 1969-11-26 | Ford Motor Co | Internal combustion engine. |
DE3935154A1 (de) * | 1989-10-21 | 1990-10-31 | Daimler Benz Ag | Auf der gleitflaeche eines betaetigungsgliedes fuer ein gaswechselventil einer hubkolbenmaschine ablaufender steuernocken |
DE19501062A1 (de) * | 1994-02-28 | 1995-08-31 | Schaeffler Waelzlager Kg | Stößel für einen Ventiltrieb einer Brennkraftmaschine |
US20010027766A1 (en) * | 1996-12-20 | 2001-10-11 | Walter Speil | Tappet for a valve mechanism of an internal combustion engine |
US5860398A (en) * | 1997-10-28 | 1999-01-19 | Koerner; Jeffrey Scott | Engine tappet |
DE19902446A1 (de) * | 1999-01-22 | 2000-07-27 | Schaeffler Waelzlager Ohg | Ventiltrieb einer Brennkraftmaschine |
US6435150B1 (en) * | 2000-07-25 | 2002-08-20 | Daimlerchrysler Corporation | Offset tappet assembly |
Also Published As
Publication number | Publication date |
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DE502004003276D1 (de) | 2007-05-03 |
US7219638B2 (en) | 2007-05-22 |
US20050235936A1 (en) | 2005-10-27 |
EP1591629B1 (de) | 2007-03-21 |
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