EP0914546A1 - Mecanisme de distribution et culasse de moteur a combustion interne - Google Patents

Mecanisme de distribution et culasse de moteur a combustion interne

Info

Publication number
EP0914546A1
EP0914546A1 EP97932761A EP97932761A EP0914546A1 EP 0914546 A1 EP0914546 A1 EP 0914546A1 EP 97932761 A EP97932761 A EP 97932761A EP 97932761 A EP97932761 A EP 97932761A EP 0914546 A1 EP0914546 A1 EP 0914546A1
Authority
EP
European Patent Office
Prior art keywords
valve
camshaft
axis
contact surface
surface area
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
EP97932761A
Other languages
German (de)
English (en)
Other versions
EP0914546B1 (fr
Inventor
Dieter Reitz
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE19629349A external-priority patent/DE19629349A1/de
Application filed by Individual filed Critical Individual
Publication of EP0914546A1 publication Critical patent/EP0914546A1/fr
Application granted granted Critical
Publication of EP0914546B1 publication Critical patent/EP0914546B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F01L1/053—Camshafts overhead type
    • 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
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0073—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "Delphi" type
    • 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 valve train and a cylinder head of an internal combustion engine equipped with such a valve train.
  • the valve train is present between its at least one stroke valve and its camshaft for controlling the variable stroke course.
  • valve drive is known from EP-Al 0 638 706, with which a valve stroke profile can be variably adjusted with regard to stroke size and stroke duration.
  • the valve train has a rocker arm, which is suspended from a pin in a pendulous manner.
  • the bolt is mounted in an elongated hole of the rocker arm and can press against the outside of the rocker arm by means of an outside
  • Eccentric take different positions.
  • the position of the rocker arm's pendulum axis differs depending on the position of the bolt within the elongated hole.
  • the rocker arm carries a roller that presses against a camshaft.
  • the rocker arm presses on a further rocker arm, referred to as a rocker arm, which in turn has a pressing effect on the lift valve.
  • the contact surface area of the rocker arm that acts on the rocker arm and thus indirectly on the lift valve comprises a different outer surface area of the rocker arm, depending on the position of the bolt within the elongated hole and thus in dependence on the respective self-aligning bearing.
  • the elongated hole pin bearing of the rocker arm has a disadvantageous effect.
  • a play of the bolt in the slot cannot be avoided for reasons of assembly.
  • This game increases when the internal combustion engine is operating due to material wear in the area of line contact between the elongated hole and the bolt.
  • this can lead to a lifting movement of the valve even when the cam with its cam base circle takes effect.
  • an undesired stroke movement in the upper resting point of the stroke valve may only be a few hundredths of a millimeter, since otherwise the hydraulic element may be inflated. The latter would have the consequence that the lift valve, for example the inlet valve, can no longer be closed completely.
  • valve train is known in which two rocker arms are positioned between the camshaft and the lift valve.
  • the rocker arms which engage in the space between the camshaft and the valve train from opposite directions are adjustable around the camshaft.
  • the valve stroke curve changes in such a way that the stroke time is always changed at the same time as the maximum stroke height, namely in the same way, that is, the stroke height and stroke duration are simultaneously increased or decreased.
  • the valve train known from DE-Al 43 22 480 requires two camshafts to adjust the valve lift of a valve.
  • the swivel path of a swivel lever pressing against the valve can be designed to be variable in order to adjust the valve lift and the opening time of the valve at the same time.
  • valve train is known, with which the valve lift course of a lift valve can only be adjusted in size.
  • the valve train has two swivel levers which engage in the space between the camshaft and the valve from opposite directions.
  • the swivel levers are arranged one above the other. While one swivel lever is rotatably mounted, the other swivel lever is designed with its axis of rotation so as to be longitudinally displaceable.
  • This longitudinally displaceable training requires a great deal of design effort.
  • the cylinder is also pierced laterally by the necessary construction elements. Apart from this, the space required in addition to the cylinder head is hardly available in today's engine compartments. Finally, the practically existing point contact between the longitudinally displaceable swivel lever and the valve stem is unsuitable for large-scale use.
  • the object of the invention is to provide a valve train which enables the valve lift course and the valve opening duration to be adjusted in a structurally satisfactory manner and with which the most compact possible cylinder head can be designed.
  • This invention is given for a valve train by the features of claim 1 and for a corresponding cylinder head by the features of claim 20.
  • the valve train according to the invention is distinguished by the use of a contact surface of its pressure transmission device which has a first surface area and an adjoining second different surface area which is arranged in this way and are designed such that a lifting movement of the lifting valve can be set only by means of the second, not by means of the first, surface area.
  • the first surface area can have a circular-cylindrical curvature, with the bearing axis as the cylinder longitudinal axis, and the second surface area can have a non-circular-cylindrical curvature that deviates therefrom.
  • the curved contact surface is followed by a third surface area, which likewise has a circular cylindrical curvature, and also with the bearing axis as the longitudinal axis of the cylinder, about which the pressure transmission device or its contact surface pivots.
  • This third surface area preferably has a radius that is larger than the radius of the above-mentioned first surface area
  • the contact surface of the pressure transmission device which presses against the lifting valve, can also be slowly displaceable along an axis of movement.
  • the first surface area can then have a flat surface running parallel to the movement axis and the second surface area can have a different surface, at least not running parallel to the movement axis.
  • this contact surface with its first surface area, that is, with its plane, to the axis of movement acts parallel contact surface on the lift valve, causes a caused by scanning the rotating camshaft cam in the axis of motion oscillating movement of the pressure transmission device and thus the contact surface in turn no stroke movement of the lift valve, such as in particular an intake valve; namely, the contact surface slides on a non-moving contact surface of the globe valve.
  • a stroke movement of the valve can only be generated when the pressure transmission device experiences a larger stroke in the axis of movement and thereby with the adjoining second surface area, which is no longer arranged parallel to the axis of movement and does not need to be even, on the contact surface of the stroke valve .
  • the phase position of the maximum stroke can be adjusted forwards or backwards depending on the arrangement of the adjusting shaft and the direction of rotation of the camshaft. These adjustment options do not require an additional phase adjuster on the camshaft.
  • the second surface area is followed by a third surface area, which in turn is flat and parallel to the movement axis.
  • This third surface area can be closer to the inlet valve than the first surface area named above.
  • the correspondingly wide-open lift valve can be left in this lift position; the contact surface rolls or slides on its contact surface with the lift valve without causing an additional positive or negative lift movement of the valve.
  • the valve can therefore remain in its preferably maximum open position over a certain period of time. Due to the fact that a phase adjustment to enable a changed opening or closing time of the lift valve in the valve drive according to the invention is not necessary, the camshaft can be driven at an unchanged constant speed. This makes it possible to provide a single camshaft for controlling both the intake and exhaust valves of an engine of an internal combustion engine. For this purpose, space is freed up above the cylinder head of this engine, in which the valve train with its pressure transmission devices can be placed. The space required above a cylinder head is practically not larger when the valve train according to the invention is arranged, so that a very slim cylinder head can be constructed.
  • the cylinder head of an internal combustion engine designed in accordance with the invention is characterized in that a first valve train is present between the single camshaft and the at least one exhaust valve, and that a second valve train, the aforementioned inventive valve train, is present between this single camshaft and the at least one intake valve.
  • a valve train according to the invention can also be used for the outlet valve.
  • This second valve train has the above-mentioned pressure transmission device, which carries out an oscillating movement with its contact surface.
  • the position of the reversal points of the oscillating contact surface can be brought about both by changing the position of a body scanning the contour of a camshaft cam and by an adjusting device additionally acting on the pressure transmission device.
  • an adjusting device additionally acting on the pressure transmission device.
  • the camshaft and adjusting shaft can be present at approximately the same height above the valves with their essential components. It is also possible to arrange the adjustment shaft between the valves below the camshaft.
  • Fig. 1 shows a cross section through a cylinder head
  • Fig. 2 shows a cross section through a cylinder head
  • FIG. 3 shows a schematic representation of the contour of a contact surface which presses on an inlet valve, of a pressure transmission device present in the valve train
  • Fig. 4 shows a cross section through a cylinder head
  • FIG. 5 shows a section through the cylinder head according to FIG. 4, with a second position of the adjusting shaft
  • Fig. 6 is a diagram with several valve lift profiles.
  • FIG. 1 A section of a cylinder head 10 with an intake valve 12 is shown in FIG. 1 of an internal combustion engine. Above the cylinder head 10 and thus also above the intake valve 12, there is an overhead camshaft 34, from which its axis 14 and one of several cams, an intake cam 16 serving to actuate the intake valve 12, can be seen.
  • a roller 35 is rotatably attached, which is needle-supported in the present case.
  • the axis of rotation 36 of the roller 35 is parallel to the axis 14 of the camshaft 34 and parallel to a further shaft 30.
  • This shaft 30 can be moved back and forth on a circumferential circle 31 with the radius R2 around the center point M (axis 14).
  • the shaft 30 is fastened on a swivel element 32.
  • This swivel element 32 can also be adjusted in a corresponding circular arc about the axis 14 with a constant radius.
  • the pivoting element 32 is adjusted relative to the respective rotational alignment of the camshaft 34 by means of a gearwheel 54 fastened on an adjusting shaft 56, which is connected to a toothing 52 present on the swivel element 32 is in meshing engagement.
  • the gear 54 is fixed on the adjusting shaft 56 in a rotationally fixed manner.
  • Swivel element 32 is adjusted relative to camshaft 34 in one or the other direction of rotation.
  • a swivel lever 74 is rotatably mounted, which carries the roller 35 at its upper end in FIG. 1, which abuts the inlet cam 16.
  • a push rod 76 presses against the pivot lever 74.
  • the other end of this push rod 76 presses against a pivot element 78 encompassing the camshaft 34 in an annular manner.
  • the pivot element 78 is fastened to the camshaft 34 in a relatively rotatable manner.
  • Rotating the inlet cam 16, for example counterclockwise, will therefore push the push rod 76 to the right, as shown in FIG. 1, and thus also the swivel element 78, likewise counterclockwise, about the axis 14 (center point M) swivel.
  • the inlet valve 12 is trimmed underside of the pivot ⁇ elements 78 has a specially shaped contact surface 80th This contact surface 80 presses on a roller 82 which is rotatably held on a further rocker arm 84.
  • This lower rocker arm 84 abuts a contact surface 22 of the inlet valve 12 from above.
  • This rocker arm 84 is pivotally mounted on a hydraulic bolt 23. Depending on how far the roller 82 is pressed from above, the valve plate 40 of the valve 12 is moved more or less far from the valve seat 42 and the inlet channel 44 is thereby opened to different lengths and lengths.
  • the contact surface 80 of the swivel element 78 has a first surface area 80.1, which has a circular-cylindrical curvature with the camshaft axis 14 as the longitudinal axis of the cylinder.
  • the radius of this cylindrical curvature has the constant dimension R1 (see also FIG. 3).
  • This surface area 80.1 is followed by a further surface area 80.2 on the contact surface 80, which has an alternating distance from the axis 14.
  • This second surface area 80.2 is followed by a third surface area 80.3, which again has a circular-cylindrical curvature, with the camshaft axis 14 as the cylinder longitudinal axis.
  • the radius of this third surface area 80.3 has the constant dimension R3.
  • R3 is larger than Rl of the first surface area 80.1.
  • the pivoting element 78 is pivoted so far counterclockwise that the third surface area 80.3 comes into contact with the roller 82, the then respectively open position of the inlet valve 12 is not changed; pivoting the swivel element 78 to the swivel area in which the third surface area 30.3 is in contact with the roller 82 does not cause a change in the stroke position of the inlet valve 12 because of the -> - cylindrical curvature of this third surface area 12.
  • the opened inlet valve 12 therefore becomes its open position maintained as long as the third surface area 80.3 in Is in contact with the roller 82. In this way, a maximally opened inlet valve 12 can be kept open uniformly over a predetermined period of time. It is only when the pivoting element 78 is pivoted back in a clockwise direction that a
  • the swivel element 32 which is not shown in more detail, can be held on a component comprising the camshaft 34, for example.
  • the adjusting shaft 56 which enables the pivoting element 32 to pivot relative to the alignment of the camshaft 34, can be rotated in the usual way.
  • the pivot lever 74 can also bear against the camshaft 34 with a correspondingly shaped sliding surface.
  • the contact surface 80 can also rest against a bucket tappet provided, for example, for hydraulic play compensation of an inlet valve.
  • FIG. 2 shows a cylinder head 10.2, each with an intake valve 12.2 and an exhaust valve 13.2.
  • a rocker arm 84 lies on the inlet valve 12.2, as has already been described above in connection with FIG. 1 for the inlet valve 12 there.
  • the roller 82 present on the rocker arm 84 bears from below on the contact surface 80, which in turn has three surface areas 80.1, 80.2 and 80.3. These three surface areas are arranged from left to right in FIG. 2, while they are arranged from right to left in FIG. 1.
  • the contact surface 80 is part of a swivel element 78.2 which surrounds an adjusting shaft 56.2 in a ring shape, rotatable relative to the same.
  • a pressure spring 92 presses against an extension 90 of this swivel element 78.2 from below, which is supported with its lower end on the cylinder head 10.2.
  • Compression spring 92 thus wants to rotate the swivel element 78.2 counterclockwise around the adjusting shaft 56.2.
  • a swivel lever 94 which projects in a threatening manner and which in the present example protrudes obliquely into the area between the two valves 12.2 and 13.2.
  • a rocking lever 96 is rotatably held.
  • the roller 35 which abuts the inlet cam 16 is rotatably supported on the one hand, and the one end of a push rod 76.2 is supported on the one hand.
  • the other end of this push rod 76.2 presses against the swivel element 78.2.
  • the push rod 76.2 thus presses clockwise against the swivel element 78.2.
  • the intake and exhaust valves 12.2, 13.2 arranged in the cylinder head 10.2 are controlled by a single camshaft, while the exhaust valve 13.2 is controlled in a manner known per se by the camshaft (camshaft axis 14) positioned above this exhaust valve 13.2 is used, the same camshaft is also used to control the opposite inlet valve 12.2.
  • the valve train required for this is arranged in the area above the two valves 12.2, 13 2 and next to this camshaft.
  • the contact surface 80 is shown enlarged again in FIG. 3.
  • a first surface area 80.1 there is a circular cylindrical surface with a constant radius R1.
  • the surface area 80.1 is followed by a second surface area 80.2, the distance from the center M of which increases.
  • the third surface area 80.3 is in turn followed by a circular cylindrical surface with a constant radius R3.
  • the area of the transition arch which is present between the two cylindrical surface areas 80.1 and 80.3, there is a different distance from the center point M.
  • the circular cylindrical surface areas 80.1 and 80.3 roll on the roller 82 (FIGS. 1, 2), there is no relative adjustment of the lift valve 12 or 12.2.
  • An adjustment of the inlet valve 12 or 12.2 takes place only in the contact area of the transition bend, the middle surface area 80.2, as is described in more detail above in connection with FIGS. 1 and 2.
  • the pivoting of the swivel elements 32, 94 not only serves to change the stroke maximum and opening duration, but also changes the phase position of the respective stroke maximum relative to the camshaft / crankshaft, so that particularly favorable motorized components are used, with a suitable design of the components and corresponding direction of rotation of the camshaft may be operating points for fuel consumption and exhaust emissions Darge ⁇ provides no additional twisting of the intake camshaft.
  • a cylinder head 210 of an internal combustion engine is shown in FIG. 4 with an intake valve 212 and an exhaust valve 213. Above the cylinder head 210 and thus also above the valves there is an overhead camshaft 215, of which a cam 216 serving to control the intake valve 212 can be seen and which rotates about its axis 217 during engine operation.
  • the cam 216 is scanned by a roller 221.
  • the roller 221 is rotatably mounted on a pin 222 by means of needles and transmits the cam stroke to the rocker arm 220.
  • the rocker arm 220 oscillates about the axis 223 of a pin 224. With its contact surface 225, the rocker arm 220 is pressed against the rounded end face 231 of the plunger 230 and sets it in an oscillating motion according to the cam stroke.
  • the plunger 230 has the shape of a cylinder and is mounted so that it can move longitudinally in a bore in the frame 265.
  • the tappet mass is reduced by a cutout 232.
  • the plunger 230 has a recess at its end opposite the end face 231, as a result of which the contact surface 238 is formed, against which a further needle-bearing roller 241 bears.
  • This contact area is divided into three surface areas.
  • the first surface area 235 is flat and runs parallel to the ram longitudinal axis 233, which also represents the axis of movement.
  • the second surface area 236 has an arbitrary contour, which, however, is not at the same time plane and runs parallel to the plunger axis 233 and opens in the direction of the plunger axis 233 into the first surface area 235 and the third surface area 237.
  • the third surface area 237 in turn runs flat and parallel to Tappet axis 233, being closer to the inlet valve than the first surface area 235.
  • the roller 241 Depending on the stroke position of the ice cream 230, the roller 241 alternately presses against the surface areas 235, 236 and 237.
  • the roller 241 transmits the valve actuation force to the rocker arm 240 via a pin 242, which, in a known manner, is supported on a hydraulic pin 248 and at its other end presses on the valve stem end of the inlet valve 212 via a contour 245.
  • the return spring 250 acts on the tappet 230 via a riveted spring plate 251 and this, the rocking lever 220 with its roller 221 and the cams 216 constantly in printing contact.
  • the return spring 250 is supported in the cylinder head 2 L0 by a screwed-in cover 218.
  • the adjusting shaft 260 is rotatably mounted in the frame 265 and the bearing cover 266 parallel to the camshaft 215.
  • a cranked lever 262 is non-rotatably connected at its broad end to the adjusting shaft 260 by a pin - this lever end does not lie in the plane of the drawing and is partially shown in the opening.
  • the lever 262 rotatably supports the pin 224 at its narrow end.
  • the pin axis 223 is the axis of rotation of the pivot lever 220 and can simultaneously be pivoted about its axis 261 by rotating the adjusting shaft 260.
  • the position shown in FIG. 5 can be reached in extreme cases.
  • the phase position of the maximum stroke on the swivel lever 220 changes. Assuming constant rotation of the camshaft 215 counterclockwise, the stroke maximum occurs earlier in the position of the adjusting shaft according to FIG. 5 than in the position shown in FIG. 4.
  • the contact surface 225 of the rocker arm 220 is designed so that during the adjustment of the adjusting shaft 260, the plunger 230 moves more and more towards the camshaft 215 in its respective rest position between the stroke events with simultaneous early adjustment of the maximum stroke.
  • This effect and the changed lever ratio on the rocker arm 220 cause the plunger 230 in the arrangement according to FIG. 5 to perform a shortened stroke at an early stroke maximum, and the roller 241 only on the surface area because of the rest position of the plunger 230 toward the camshaft 215 235 rolls back and forth so that there is no lifting movement at the inlet valve 212.
  • the roller 241 reaches the surface area 236 after a very slight stroke movement of the tappet 230, so that a stroke movement of the inlet valve 212 takes place, and finally the surface area 237, the valve remaining at the maximum stroke height.
  • the roller 241 alternately passes through the surface regions 235 and 236 in such a way that different portions of the stroke movement of the tappet 230 on the non-valve-opening surface region 235 or on the valve-opening surface region 236 are eliminated. Therefore, twisting the adjusting shaft 260 along with the change in the valve opening and closing times causes a continuous change in the stroke amplitude and the opening duration of the intake valve 212.
  • 6 shows an example of a family of valve lift curves as can be generated by means of the valve drive shown in FIGS. 4 and 5 with the camshaft rotating to the left. In this case, the valve opens at an almost constant phase position, while the stroke amplitude increases continuously with the opening time. When the surface area 237 is reached by the roller 241, the stroke amplitude remains constant, while the opening duration continues to increase. This corresponds to an extension of the stroke curve, as can be seen on the curve with a stroke amplitude of 10 millimeters.
  • the outlet valve 213 is actuated via a rocker arm 270 known per se. It is rotatably mounted on a shaft 275 and transmits its movement via a hydraulic valve lash adjuster 274 to the exhaust valve 213.
  • the cam is scanned by a needle-bearing roller 271 and a bearing pin 272. With a left-rotating camshaft 215 and corresponding valve timing, the roller 271 can also den otherwise scan the cam 216 of the camshaft 215 assigned to the intake valve. In other cases, it is possible to provide an additional exhaust cam on the camshaft 215 to the side of the intake cam 216 and to arrange the roller 271 laterally offset on the rocker arm 270.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention concerne un mécanisme de distribution de moteur à combustion interne, situé entre au moins une soupape de levage (12) et un arbre à cames (34), pour assurer la commande de la marche variable de levée. Le mécanisme de distribution comprend un dispositif de transmission de pression placé de manière à appuyer sur la soupape de levage (12), ainsi qu'un élément de contact (35) situé sur une came (16) de l'arbre à cames (34) et qui produit un mouvement oscillant du dispositif de transmission de pression, lors de son changement de position dû à la rotation de la came (16). Le dispositif de transmission de pression présente une surface de contact (80) par l'intermédiaire de laquelle s'effectue la transmission de pression. La surface de contact (80) qui peut pivoter autour de l'axe du palier (14) comporte d'une part une première zone superficielle (80,1) présentant une courbure cylindrique circulaire, l'axe du palier (14) constituant l'axe longitudinal du cylindre, et d'autre part, une seconde zone superficielle (80,2) qui se raccorde à la première zone superficielle (80,1) et ne présente pas de courbure cylindrique circulaire.
EP97932761A 1996-07-20 1997-07-18 Mecanisme de distribution et culasse de moteur a combustion interne Expired - Lifetime EP0914546B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19629349 1996-07-20
DE19629349A DE19629349A1 (de) 1996-07-20 1996-07-20 Ventiltrieb und Zylinderkopf einer Brennkraftmaschine
DE19640520A DE19640520A1 (de) 1996-07-20 1996-10-01 Ventiltrieb und Zylinderkopf einer Brennkraftmaschine
DE19640520 1996-10-01
PCT/DE1997/001514 WO1998003778A1 (fr) 1996-07-20 1997-07-18 Mecanisme de distribution et culasse de moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0914546A1 true EP0914546A1 (fr) 1999-05-12
EP0914546B1 EP0914546B1 (fr) 2001-05-16

Family

ID=26027691

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97932761A Expired - Lifetime EP0914546B1 (fr) 1996-07-20 1997-07-18 Mecanisme de distribution et culasse de moteur a combustion interne

Country Status (3)

Country Link
EP (1) EP0914546B1 (fr)
DE (3) DE19640520A1 (fr)
WO (1) WO1998003778A1 (fr)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6412460B1 (en) 1997-06-24 2002-07-02 Honda Giken Kogyo Kabushiki Kaisha Valve operating system in internal combustion engine
US6019076A (en) * 1998-08-05 2000-02-01 General Motors Corporation Variable valve timing mechanism
EP1013898B1 (fr) * 1998-12-22 2005-08-03 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
GB2357131A (en) * 1999-12-09 2001-06-13 Mechadyne Internat Plc Valve actuating mechanism
DE10006018B4 (de) 2000-02-11 2009-09-17 Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10006016B4 (de) * 2000-02-11 2009-08-06 Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10052811A1 (de) 2000-10-25 2002-05-08 Ina Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10123186A1 (de) * 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Ventiltrieb-Vorrichtung zur variablen Hubverstellung eines Gaswechselventils einer Brennkraftmaschine
DE10136612A1 (de) * 2001-07-17 2003-02-06 Herbert Naumann Variable Hubventilsteuerungen
DE10155007A1 (de) * 2001-11-06 2003-05-15 Herbert Naumann Hubventilsteuerung
DE10221133A1 (de) * 2002-05-13 2003-11-27 Thyssen Krupp Automotive Ag Antriebs- und Verstellsystem für variable Ventilsteuerungen
US6868811B2 (en) 2002-06-13 2005-03-22 Delphi Technologies, Inc. Frameless variable valve actuation mechanism
DE10312961C5 (de) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
DE10354428A1 (de) * 2003-11-21 2005-06-23 Bayerische Motoren Werke Ag Verfahren zum Betrieb einer Brennkraftmaschine
DE112004001267B4 (de) * 2004-03-23 2010-06-24 Mitsubishi Fuso Truck And Bus Corp. Variabler Ventiltrieb eines Verbrennungsmotors
DE102005042258B4 (de) * 2004-09-07 2009-07-09 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen mit zwischen Zylinderbänken angeordneter Nockenwelle
DE102005012081B4 (de) * 2005-03-03 2021-09-16 Kolbenschmidt Pierburg Innovations Gmbh Variable mechanische Ventilsteuerung einer Brennkraftmaschine
WO2006092312A1 (fr) 2005-03-03 2006-09-08 Hydraulik-Ring Gmbh Commande mecanique variable de soupapes d'un moteur a combustion interne
DE102005010182B4 (de) * 2005-03-03 2016-05-25 Kolbenschmidt Pierburg Innovations Gmbh Variabel mechanische Ventilsteuerung einer Brennkraftmaschine
JP4265573B2 (ja) * 2005-06-09 2009-05-20 三菱自動車工業株式会社 内燃機関の可変動弁装置
JP4507997B2 (ja) * 2005-06-15 2010-07-21 三菱自動車工業株式会社 内燃機関の可変動弁装置
DE102005028542A1 (de) * 2005-06-17 2006-12-28 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen
JP4380695B2 (ja) * 2006-12-18 2009-12-09 トヨタ自動車株式会社 可変動弁機構付き内燃機関
DE102016004531A1 (de) * 2016-04-13 2017-10-19 Man Truck & Bus Ag Variabler Ventiltrieb mit einem Kipphebel

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2629554A1 (de) * 1976-07-01 1978-01-12 Daimler Benz Ag Lastregelung fuer gemischverdichtende brennkraftmaschinen mit ventilsteuerung
DE2951361A1 (de) 1979-12-20 1981-07-02 Bayerische Motoren Werke AG, 8000 München Ventiltrieb mit hubverstellung fuer brennkraftmaschinen
FR2472078A1 (fr) * 1979-12-21 1981-06-26 Baguena Michel Distribution variable pour moteur a quatre temps
FR2519375B1 (fr) * 1981-12-31 1986-07-11 Baguena Michel Distribution variable pour moteur a quatre temps
US4582029A (en) 1982-09-10 1986-04-15 Mazda Motor Corporation Valve timing control system for internal combustion engine
JPS60178911A (ja) * 1984-02-24 1985-09-12 Honda Motor Co Ltd 多気筒内燃機関のｏ．ｈ．ｃ．型動弁装置
JPH0830403B2 (ja) * 1989-12-21 1996-03-27 卓也 松本 エンジンのバルブ駆動装置
DE4209062C1 (fr) * 1992-03-20 1993-04-01 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4322480C2 (de) 1993-07-06 1996-05-02 Meta Motoren Energietech Vorrichtung zur variablen Ventilsteuerung von Brennkraftmaschinen
EP0638706A1 (fr) 1993-08-05 1995-02-15 Bayerische Motoren Werke Aktiengesellschaft Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne
DE4342806A1 (de) 1993-12-15 1995-06-22 Lange Peter Ventiltrieb mit Hubverstellung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9803778A1 *

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DE19640520A1 (de) 1998-04-09
WO1998003778A1 (fr) 1998-01-29
EP0914546B1 (fr) 2001-05-16
DE19780736D2 (de) 1998-10-01
DE59703557D1 (de) 2001-06-21

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