EP1245797A2 - Desmodromischer Ventiltrieb - Google Patents
Desmodromischer Ventiltrieb Download PDFInfo
- Publication number
- EP1245797A2 EP1245797A2 EP02006133A EP02006133A EP1245797A2 EP 1245797 A2 EP1245797 A2 EP 1245797A2 EP 02006133 A EP02006133 A EP 02006133A EP 02006133 A EP02006133 A EP 02006133A EP 1245797 A2 EP1245797 A2 EP 1245797A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- valve
- enclosing
- enclosing element
- region
- 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.)
- Withdrawn
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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—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
- 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
- F01L1/30—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of positively opened and closed valves, i.e. desmodromic valves
Definitions
- the invention relates to a valve train, in particular for internal combustion engines from Motor vehicles with at least one driven cam element, the Circumferential surface a convex base circle area and a convex cam area has, and with a displaceable or pivotable by the cam element Cam follower element, in particular a valve lifter, the cam element is rotatably arranged in a flexible enclosing element which with the Cam follower is movably connected.
- Modern internal combustion engines are said to have high torque across the entire speed range reach (e.g. 100 Nm per liter cubic capacity).
- high cylinder fillings Air and fuel
- the filling is determined by the valve lift, the released valve area (valve diameter), determines the channel cross-section and the flow.
- the valve lift will geometrically limited by the piston and by the other valve when entering and leaving Exhaust valves are open at the same time.
- Extending the closing time is also limited as this is in the Overlap phase, when inlet and outlet are open at the same time, to fill losses (Fresh gas flows into the exhaust) and backflows if the valve is closed too late leads into the intake system. Long opening times postpone the Performance in higher speed ranges, i.e. the engine loses at low speeds in power (torque), which is not desirable or only makes sense for racing engines gives.
- valve spring - which multiplies this acceleration counteracts with the valve mass plus other oscillating parts - stronger be interpreted, which means more surface pressure, alternating torque and load of the Valve train results. You don't want that. This leaves only for "filling" the combustion chamber there is still a larger stroke increase per time or cam angle unit, i.e. the The valve must be opened from the valve seat as quickly as possible.
- the increase in stroke per angular unit can be increased by increasing the base circle diameter.
- the radius of the cam base circle would have to be in the range above 30 mm, which is no longer sensible in terms of design.
- Useful cam base radii are in the range from 16 to 20 mm. If you execute the tangent cam with 25 mm, the accelerations are too low (50 - 60 mm / rad 2 ), filling and thus torque are given away.
- a second way to achieve high accelerations, but only at Rocker arm valve drives is achievable is the formation of a concave Transition area between the covex base circle area and the convex Cam area, i.e. the base circle angle and the cam angle are due to the Indentation enlarged. This is the case for direct valve drives with bucket tappets senseless, since the surface of the tappet is too large and the concave transition area bridged.
- the return spring may be a force counteracting the valve opening required to ensure valve clearance compensation for the closed position. This can be mechanically via a spring between two parts that are movable relative to each other of the valve lifter, such as US 1,238,175 A or US 1,937,152 show.
- the Cam follower does not move as long as the connection area of the Enclosure element with the cam follower element at the base circle area of the rotating cam element is then from the axis of rotation of the Removed cam element in the radial direction and finally brought it back again, during the cam area of the cam element the connection area of the Enclosure element happens with the cam follower.
- the moveable Connection of the enclosing element with the cam follower leaves the Swiveling or tilting movement of the enclosing element in the cam area, so that the required freedom of movement of the cam follower in its sliding or Swivel bearing is maintained.
- the enclosing element is in the first embodiment formed from two flexible rings, between which to reduce the Friction needle-shaped rolling elements are provided.
- a second version shows a Plastic tape with an inner ceramic sliding layer.
- One advantage of positive control by a containment element is high Achieve accelerations and decelerations without overloading the valve train to be able to. For this only a convex, at most a tangent cam shape appears sensible, since the enclosing element does not automatically turn into a concave Can insert transition area.
- the tangent cam shape provides meaningful base circle dimensions not the desired acceleration values and is giving away an important advantage of forced control, namely fast - and thus thermodynamically ideal - to open. High delays at maximum Valve lift can be achieved, but the filling loss can be caused by slow opening is no longer compensated for. So it loses Forced control of attractiveness.
- the positive control allows a slightly larger one Base circle radius up to 25 mm as the cam follower cams because of the loss of installation space overcompensated due to the larger base radius due to the missing spring etc. becomes.
- the invention has now set itself the task of positively controlling the input mentioned type to create the high acceleration and deceleration values allows.
- this is achieved in that between the base circle area and a concave transition area is provided for the cam area of the cam element is in which the enclosing element through one counteracting the valve opening Force can be impressed.
- a spring can be used that is much lighter than a valve spring can not be positively controlled valves, and about valve lash adjuster described corresponds, whereby the cam follower presses on the enclosing element.
- a tensile force is generated or introduced in the enclosing element in the direction of its extension and diverted there.
- the enclosing element at the connection point with the cam follower element has an elevation projecting inwards towards the cam element.
- the elevation projecting inwards lies in the two convex peripheral regions of the cam element, so that the enclosing element forms an outward projection at the connection point of the cam follower element.
- the tensile forces in the flexible enclosing element thereby generate a force towards the peripheral surface of the cam element, which allows the inward elevation to enter the concave transition region as soon as it rotates past the elevation.
- the elevation as a component of the encircling element is now pressed outward from the cam area and, due to the enlarged cam angle with a steeper increase, causes the greater stroke increase per cam angle unit and the high acceleration values. Acceleration values of 80 to 85 mm / rad 2 can be easily achieved.
- the elevation protruding inwards offers space for a holder of the cam follower element, for example a bearing pin, a bearing bush or the like.
- a holder of the cam follower element for example a bearing pin, a bearing bush or the like.
- the holder can also be arranged on the outside of the cam follower element, however requires additional space there.
- the inward elevation can also be a pressure distribution pad comprise, which has an approximately triangular cross section, and in particular consists of a deformable material.
- the pressure distribution pad causes one Reduction of the surface pressure on the cam peripheral surface. He can from one rubbery, slightly elastic material, but it can also be with a liquid or filled with a gel to adhere to the changing cavity cross sections adapt.
- the pressure distribution pad also provides noise reduction.
- the general rule is that the inertial forces occurring when opening and closing the valve always try the enclosing element in the concave transition area to push in. These mass forces naturally only occur when the machine is running Engine on, and are speed dependent. From an engine speed of around 2000 revolutions The mass forces per minute are sufficient, the necessary tensile forces in the Initiate enclosing element, so that from this speed the high acceleration values for the valve opening can be achieved (the required mass forces produce). At lower speeds, especially when the engine is idling, they are Mass forces too low to move the enclosing element into the concave transition area to press.
- the enclosing element is biased towards contraction is.
- the length of the enclosing element shortens as soon as the Alternative space of the concave transition area for the inward elevation is reached.
- the preload can be slight, since the shortening is normal Cam shapes at about half a percent of the length of the enclosing element lies, so that the material stresses are rather small.
- the preload can also be small because only the initial range up to about 2000 Revolutions per minute must be covered, and then sufficient Mass forces are present.
- a first embodiment of the enclosing element therefore provides at least one elastically stretchable area.
- the enclosing element is preferably formed at least in two layers, one of the two layers being formed from an elastically stretchable material whose modulus of elasticity is up to 4000 N / mm 2 .
- the modulus of elasticity is preferably between 800 and 1200 N / mm 2 .
- Such an encircling element consists in particular of at least two loops connected to one another, the second loop extending in the circumferential direction of the cam element from high-tensile fibers, for example from kevlar, glass, carbon, high modulus polyethylene, polyester, boron, aramid fibers or the like , has essentially length-constant fibers or combinations of these fibers, and serves as a limitation of elongation.
- a simple production of the solidified layer results when the high tensile strength Fibers are arranged in a seamlessly closed surface material, which in a textile roundwork technology is manufactured (circular knitting, round weaving, round knitting or the like.).
- the enclosing element preferably has a sliding layer which acts as an inner third Loop made of a low-friction material or through a coating, for example Evaporation of the inner layer can be formed.
- the cam element and / or the enclosing element consists of one Material with a low-friction or low-friction coated surface, for example, polytetrafluoroethylene (PTFE), a vapor-deposited hard material, one Silicone, molybdenum sulfide or the like, lubrication of the sliding surfaces may be necessary, thus the peripheral surface of the cam element and the adjacent inner surface of the enclosing element is not necessary.
- PTFE polytetrafluoroethylene
- the cam element radially to the axis of rotation has at least one oil hole on the circumference of the Cam element opens within the flexible enclosing element. Since that Enclosure element is not twisted, is also an external oil supply through the Enclosure element conceivable via a flexible line.
- a contactless arrangement of the enclosing element can also be used be provided if, for example, a magnetized inner Sliding layer is formed, which consists of an equipolar magnetized outer layer repels the cam element.
- the masses to be accelerated are essential in the valve train according to the invention reduced.
- the use of light metals, ceramics or plastic for the valve and / or the cam follower element allow a reduction in those to be accelerated and decelerating masses from 50% to 80% of the value of a valve lifter Return spring and hydraulic backlash compensation.
- the valve can be made shorter and installation space can be saved.
- the cam element can also be made smaller. The same goes for training of plastic cam elements or completely made of plastic, for example Camshafts produced by injection molding can be realized. Use too other lightweight materials for the production of camshafts or cam elements, for example aluminum becomes possible. Because of the mass reduction and The lubrication is expected to save 5% or more.
- the enclosing element is in this version with one or two layers, i.e. it has a loop made of high tensile strength Fibers or fabric on the inside with the sliding layer steamed or provided with its own loop made of low-friction material.
- the length of the enclosing element corresponds to the circumferential length of the Cam element, the elevation approximately the excess compared to Enclosure length corresponds, so that the enclosing element is a base circle area and lying loosely on the cam area with at most little play Surrounds cam element.
- the elevation enters the concave transition area the enclosing element becomes too long and "shakes" briefly until the first section of the stroke has compensated for the excess.
- the transition from the convex cam area to the convex Base circle area can be formed directly in the usual way or one include a straight tangential section, i.e. there is no need for a concave transition area be provided. But if there is also a concave transition area is formed, the closing acceleration becomes due to the extension of the cam area increased until the inward elevation of the enclosing element enters the concave transition area. The sharper transition to the The base circle area ensures that the valve closes securely, since it acts as a cam element directed force is increased. If only the mass forces Influence enclosing element, it is in the closed position after a short Calming phase of the enclosing element without external stress. This helps the compression and explosion pressure in the cylinder, the valve disc close to the seat hold.
- the valve train comprises a cam element 2 fastened on a carrier shaft 1, which a base circle area 71, a cam area 72 and a concave transition area 73 has.
- the center of curvature of the base circle area 71 and The point of curvature of the central part 76 of the cam region 72 is in each case the axis 8 of the carrier shaft 1.
- the cam element 2 is driven about the axis 8 and runs within a flexible enclosing element 4, which has a Junction 12 is connected to a cam follower 10, which, as in the 1 to 4, a valve stem 11 of a tappet valve, the valve plate 69 interacts with a valve seat 70.
- valve plate 69 In the closed position of the valve according to FIG. 1, the valve plate 69 lies in the sealing Valve seat 70. Will the cam element 2 in the direction of arrow B in the position 2 rotated, the connection point 12 slides along the base circle region 71 and reaches the concave transition area 73. During this partial rotation remains the valve plate 69 in the valve seat since there is no stroke and the valve stem 11 does not is moved. 3 continues to slide into the position according to FIG 12 via the transition region 73 into the cam region 71, with the concave curvature is a relatively quick release of the valve plate 69 from the valve seat 70 is reached. 3 shows that position of the connection point 12 at which the There is a change from valve acceleration to valve deceleration, i.e.
- Fig. 4 is the position of the junction 12 at the beginning of the central area 76 shown in which the valve opening movement ends and the maximum open position given is. There is no further stroke along the central part 76, similar to in the base circle area 71.
- the process is reversed, i.e. begins at the end of the central part 76 the closing acceleration, which in the mirrored position to Fig. 3 in the closing delay replaced.
- Fig. 7 shows a graph in which the size and direction the forces acting on the enclosing element 4 are shown by arrows are.
- the encircling element 4 since it is articulatedly connected to the valve stem 11 via the connection point 12, cannot rotate with the cam element 2, but is only continuously pulsed deformed.
- it has a multi-layer closed loop which has an inner sliding layer 22 made of a friction-reducing material (PTFE, silicone, MoS 2 or the like), a middle layer 67 made of an elastically stretchable material , and an outer layer 66 of a tensile material.
- the length of the middle layer 67 made of the elastically dehribaren, for example rubber-like material corresponds in the unstretched state to the length of the enclosure of the cam element 2, but is preferably slightly shorter.
- the material preferably has an elastic modulus between 600 and 2000 N / mm 2 , in particular between 800 and 1200 N / mm 2 .
- the outer layer 66 of the tensile material has a length that extends 3 and is therefore larger than the length of the enclosure of the cam element 2.
- the length corresponds approximately to the circumferential length of the Cam element 2 with only one concave transition region 73 for the opening phase, even if the cam member 2 has a second concave transition region in the closing phase.
- Outer layer 66 is preferably one in one textile roundwork technology (circular weaving, circular knitting, round knitting or the like) seamlessly Manufactured fabric tape, which is carbon, kevlar, glass, boron, Contains polyethylene, polyester, aramid threads or fibers or the like, since this has a high Have tensile strength, oil and temperature resistance.
- the tensile threads can weft threads of the fabric tape running in the circumferential direction of the cam element or additional threads that are connected to the fabric tape.
- the elastically stretchable layer 67 can be connected to the tensile layer 66, be glued, for example.
- the enclosing element formed from the two layers 4 thus has two circumferential lengths, the smaller circumferential length being the Length of the unstretched, elastically stretchable layer 67 and the greater circumferential length is given by the length of the tensile outer layer 66, the one Elongation limit for the stretchable layer 67 represents. In the unstretched state are therefore the tensile threads in zigzag, wavy or the like. The effect of Elongation limitation is particularly necessary in the position shown in FIG. 3, in which the Inertial forces of the maximally accelerated valve that is now to be decelerated Need to become.
- the enclosing element 4 has one with an inward elevation 74 provided area in which the connection point 12 for the articulation of the Cam follower element 10 is provided, which is shown enlarged in Fig. 5.
- the Junction 12 carries a holder, for example a bearing bush 68, a Bearing pin 14 (Fig. 6) or the like.
- the Connection with the valve stem 11 or the like.
- the upper end of the valve stem 11 can be bifurcated and have two eyelets that on the two ends of the enclosing element 4 projecting laterally Bearing pin 14 are stored.
- the bearing pin can therefore also be stretched elastically Layer embedded. If a bearing bush 68 is provided, the bearing pin can also formed in two parts and inserted into the bearing bush 68 from both sides his.
- the bump 74 on the inside of the joint 12 includes a pressure distribution structure or structure, in particular a pressure distribution pad 75, the has an approximately triangular cross-sectional shape.
- the innermost layer is the friction-reducing one Layer 22 or coating provided.
- the pressure distribution pad 75 may be off a rubber-like, elastic material, but it is preferred with liquid or filled with a gel so that it is deformable but inelastic, and conforms to different Cavity cross-sections better adapted (Fig. 2, 3).
- the elevation 74 and the tensile forces generated in the enclosing element 4 act on the prestressing of the elastically stretchable layer 67 and / or the valve mass forces 8 lead to a force directed towards the cam element 2, as long as the elevation on a convex or flat area of the cam circumference slides.
- the concave transition region 73 presses to Cam element 2 directed force the elevation in the resulting cavity, so that the enclosing element 2 can contract (Fig. 9).
- the one for the opening significant internal contact surface of the enclosing element 4 of the valve thereby interacts with the peripheral surface of the cam portion 72, although the Layers 66 and 67 evenly span the concave transition region 73 at a distance.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
Claims (14)
- Ventiltrieb, insbesondere für Brennkraftmaschinen von Kraftfahrzeugen, mit mindestens einem angetriebenen Nockenelement (2), dessen Umfangsfläche einen konvexen Grundkreisbereich und einen konvexen Nockenbereich aufweist, und mit einem vom Nockenelement (2) verschieb- oder verschwenkbaren Nockenfolgeelement (10), insbesondere einem Ventilstößel, wobei das Nockenelement (2) drehbar in einem flexiblen Umschließungselement (4) angeordnet ist, das mit dem Nockenfolgeelement (10) beweglich verbunden ist, dadurch gekennzeichnet, daß zwischen dem Grundkreisbereich (71) und dem Nockenbereich (72) des Nockenelementes (2) ein konkaver Übergangsbereich (73) vorgesehen ist, in den das Umschließungselement (4) durch eine der Ventilöffnung entgegenwirkende Kraft eindrückbar ist.
- Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß der Grundkreisbereich (71) des Nockenelementes (2) und ein zentraler Teil (76) seines Nockenbereiches (72) einen gemeinsamen Krümmungsmittelpunkt aufweisen, der in der Achse (8) des Nockenelementes (2) liegt.
- Ventiltrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Umschließungselement (4) an der Verbindungsstelle (12) mit dem Nockenfolgeelement (10) eine nach innen zum Nockenelement (2) vorstehende Erhebung (74) aufweist.
- Ventiltrieb nach Anspruch 3, dadurch gekennzeichnet, daß in der nach innen gerichteten Erhebung (74) des Umschließungselements (4) ein Lagerstift (14) für das Nockenfolgeelement (10) angeordnet ist.
- Ventiltrieb nach Anspruch 3 oder 4, dadurch gekennzeichnet, daß die nach innen gerichtete Erhebung (74) des Umschließungselements (4) einen Druckverteilungspolster (75) umfaßt.
- Ventiltrieb nach Anspruch 5, dadurch gekennzeichnet, daß der Druckverteilungspolster (75) aus einem verformbaren Material besteht.
- Ventiltrieb nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, daß das Umschließungselement (4) auf Kontraktion vorgespannt ist.
- Ventiltrieb nach Anspruch 7, dadurch gekennzeichnet, daß das Umschließungselement (4) aus zumindest zwei unterschiedlichen Materialien zusammengesetzt ist, von denen ein Material elastisch dehnbar ist.
- Ventiltrieb nach Anspruch 8, dadurch gekennzeichnet, daß das Umschließungselement (4) zumindest zweischichtig ist, und das elastisch dehnbare Material die Außenschicht bildet.
- Ventiltrieb nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß der elastisch dehnbare Bereich aus einem Material mit einem E-Modul zwischen 1 und 4000 N/mm2 gebildet ist.
- Ventiltrieb nach Anspruch 10, dadurch gekennzeichnet, daß der E-Modul zwischen 600 und 2000 N/mm2, insbesondere zwischen 800 und 1200 N/mm2 liegt.
- Ventil nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, daß das Umschließungselement (4) sich in Umfangsrichtung des Nockenelementes (2) erstreckenden Fäden aus hochzugfesten Fasern aufweist.
- Ventiltrieb nach Anspruch 12, dadurch gekennzeichnet, daß die hochzugfesten Fasern in einem nahtlos geschlossenen Flächenmaterial angeordnet sind, das in einer textilen Rundarbeitstechnik hergestellt ist.
- Ventiltrieb nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß das Umschließungselement(4) eine innere Gleitschicht (22) aufweist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT4792001 | 2001-03-26 | ||
AT4792001 | 2001-03-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1245797A2 true EP1245797A2 (de) | 2002-10-02 |
EP1245797A3 EP1245797A3 (de) | 2003-01-08 |
Family
ID=3674904
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02006133A Withdrawn EP1245797A3 (de) | 2001-03-26 | 2002-03-19 | Desmodromischer Ventiltrieb |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP1245797A3 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10306428A1 (de) * | 2003-02-15 | 2004-08-26 | Contitech Antriebssysteme Gmbh | Zwangsgesteuerter Ventiltrieb mit endlosem Koppelelement |
DE102004026430B3 (de) * | 2004-05-29 | 2005-09-01 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
EP1752621A1 (de) * | 2005-08-13 | 2007-02-14 | Dr. Ing. H.C.F. Porsche Aktiengesellschaft | Zwangsgesteuerter Ventiltrieb |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2184783A (en) * | 1985-12-14 | 1987-07-01 | Stidworthy Frederick M | Poppet valve gear |
DE3700715A1 (de) * | 1986-01-22 | 1987-07-23 | Volkswagen Ag | Zwangssteuerung fuer ein ventil |
WO2001012958A1 (de) * | 1999-08-12 | 2001-02-22 | Stefan Battlogg | Ventiltrieb, insbesondere für brennkraftmaschinen von kraftfahrzeugen |
EP1205643A1 (de) * | 2000-11-13 | 2002-05-15 | Stefan Battlogg | Ventieltrieb für eine Verbrennungskraftmaschine |
-
2002
- 2002-03-19 EP EP02006133A patent/EP1245797A3/de not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2184783A (en) * | 1985-12-14 | 1987-07-01 | Stidworthy Frederick M | Poppet valve gear |
DE3700715A1 (de) * | 1986-01-22 | 1987-07-23 | Volkswagen Ag | Zwangssteuerung fuer ein ventil |
WO2001012958A1 (de) * | 1999-08-12 | 2001-02-22 | Stefan Battlogg | Ventiltrieb, insbesondere für brennkraftmaschinen von kraftfahrzeugen |
EP1205643A1 (de) * | 2000-11-13 | 2002-05-15 | Stefan Battlogg | Ventieltrieb für eine Verbrennungskraftmaschine |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10306428A1 (de) * | 2003-02-15 | 2004-08-26 | Contitech Antriebssysteme Gmbh | Zwangsgesteuerter Ventiltrieb mit endlosem Koppelelement |
DE102004026430B3 (de) * | 2004-05-29 | 2005-09-01 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
EP1600610A3 (de) * | 2004-05-29 | 2008-08-20 | Dr. Ing. h.c. F. Porsche Aktiengesellschaft | Ventiltrieb für eine Brennkraftmaschine |
EP1752621A1 (de) * | 2005-08-13 | 2007-02-14 | Dr. Ing. H.C.F. Porsche Aktiengesellschaft | Zwangsgesteuerter Ventiltrieb |
Also Published As
Publication number | Publication date |
---|---|
EP1245797A3 (de) | 2003-01-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102009048621B4 (de) | Ventiltrieb für Gaswechselventile mit Verspannung von Grundnockenwelle und Nockenträger in Umfangs- oder Drehrichtung | |
DE3245246C2 (de) | Hubkolbenmaschine mit einem Exzenter-Triebwerk | |
DE69511808T2 (de) | Ventilsteuerungsvorrichtung für mehrzylindrige Brennkraftmaschine | |
DE10230108B4 (de) | Vorrichtung zum Verstellen des Hubs eines von einer Nockenwelle betätigten Ventils | |
DE19859564B4 (de) | Variable Ventilverstellvorrichtung | |
DE4013633C2 (de) | ||
DE2822147B2 (de) | Nockenwellenanordnung, insbesondere für eine Brennkraftmaschine | |
DE102007027979A1 (de) | Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit Nockenwellen-Tunnellager | |
DE69305894T2 (de) | Ventilantrieb für eine Brennkraftmaschine | |
EP1206628A1 (de) | Ventiltrieb, insbesondere für brennkraftmaschinen | |
DE4135257C2 (de) | Vorrichtung zur Betätigung der Ventile in Verbrennungsmotoren mittels umlaufender Nocken | |
EP0865566B1 (de) | Ventiltrieb einer brennkraftmaschine | |
EP1245797A2 (de) | Desmodromischer Ventiltrieb | |
WO2003083269A1 (de) | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung | |
EP0797726B1 (de) | Ventiltrieb einer brennkraftmaschine | |
DE102004008389A1 (de) | Hubvariabler Ventiltrieb für eine Brennkraftmaschine | |
EP1619362A2 (de) | Ventiltrieb einer Brennkraftmaschine | |
EP1608852B1 (de) | Vorrichtung zur variablen bet tigung der gaswechselventile v on verbrennungsmotoren und verfahren zum betreiben einer derartigen vorrichtung | |
DE4300684C2 (de) | Ventiltrieb zur variablen Steuerung von Brennkraftmaschinen | |
DE102008015218A1 (de) | Ventilmechanismus eines Motors | |
DE4230809C2 (de) | Ventilsteuerung für Brennkraftmaschinen | |
DE3802528A1 (de) | Drehzahlreduktionseinrichtung | |
EP1247946A2 (de) | Ventiltrieb | |
EP1591629B1 (de) | Nocken mit einer Nut zur Steuerung der Rotation eines Nockenfolgeelements | |
DE3512035A1 (de) | Einrichtung zur ventilbetaetigung |
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 |
Kind code of ref document: A2 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
17P | Request for examination filed |
Effective date: 20030528 |
|
AKX | Designation fees paid |
Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
17Q | First examination report despatched |
Effective date: 20031124 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20051001 |