EP0097665A1 - Verstellbare ventilsteuerung einer viertakt-brennkraftmaschine. - Google Patents

Verstellbare ventilsteuerung einer viertakt-brennkraftmaschine.

Info

Publication number
EP0097665A1
EP0097665A1 EP83900048A EP83900048A EP0097665A1 EP 0097665 A1 EP0097665 A1 EP 0097665A1 EP 83900048 A EP83900048 A EP 83900048A EP 83900048 A EP83900048 A EP 83900048A EP 0097665 A1 EP0097665 A1 EP 0097665A1
Authority
EP
European Patent Office
Prior art keywords
cam
roller
valve
axis
movement
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
EP83900048A
Other languages
English (en)
French (fr)
Other versions
EP0097665B1 (de
Inventor
Michel Baguena
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
Application filed by Individual filed Critical Individual
Publication of EP0097665A1 publication Critical patent/EP0097665A1/de
Application granted granted Critical
Publication of EP0097665B1 publication Critical patent/EP0097665B1/de
Expired 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
    • F01L1/08—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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/044—Reciprocating 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
    • F01L1/02—Valve drive
    • F01L1/10—Valve drive by means of crank-or eccentric-driven rods
    • 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
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • 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
    • F01L13/0021—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 rocker arm ratio
    • 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
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0047—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other
    • 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
    • F01L2013/0068—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 "BMW-Valvetronic" 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention relates to a device for internal combustion engines which makes it possible to vary the opening time and the lifting of the dispensing valves.
  • the static cam (5) occupies here the position corresponding to the greatest duration of opening and lifting of the valve (6).
  • the rod (i), the roller (4), the latch (5), the valve (6) and the spring (7) determine in the representation in solid lines, the position of maximum lifting of the valve (6) and dotted, the opening start and end of closing positions of the valve (6).
  • the range of movement of the valve (6) is greater than 150 degrees, which represents for a four-stroke engine where the shaft (2) rotates at half speed, a cam angle greater than 300 DV (DV: Degrees reported to the crankshaft; to the engine output shaft).
  • DV Degrees reported to the crankshaft; to the engine output shaft.
  • German patent describes a mechanism comprising an alternating cam driven by another rotating cam, and the adjustment mode of which consists in offsetting the driving camshaft, so as to cause a relative rotation of the alternating cam relative to the latch acting on the valve.
  • the eccentricity of the driving camshaft is a means of adjustment which makes it impossible to use a single camshaft for intake and exhaust and which, above all, still leads to an embodiment which is much too bulky.
  • the invention makes it possible in particular to eliminate these drawbacks and achieves this object with a valve control device constructed according to the principle of a kinematic chain comprising two cams; that leading in rotation of fixed axis communicates to a balance the invariable primary alternative movement from which suitable means allow the use of all or part of the profile of the cam of the secondary movement of lifting of the valve which according to the embodiment of the invention can be static, alternative or tilting.
  • the invariable laws of the reciprocating movement back and forth can be rigorously symmetrical or very distinct; it follows that the opening and closing phases of the valve are respectively symmetrical or clearly asymmetrical. For very short valve openings, it is desirable to limit the maximum valve lift in order to avoid considerable efforts in the distribution elements.
  • the invention offers the greatest possible choice for the law of alternative primary movement, the minimized amplitude of which is fully used by the second cam of the valve lifting movement during the greatest opening time. This advantageous property results from the existence of the stop range of the reciprocating movement, corresponding to the neutral part of the rotating cam. The size of the device is thus reduced in large proportionso
  • the driving cam takes the form of a disc cam.
  • a disc cam follower In the case of a bilateral connection, a disc cam follower generally ensures the return of the reciprocating movement.
  • the use for example of a grooved cam is to be avoided in particular because of the machining disadvantages.
  • the contacts with the aforementioned disc cams can be made by means of pads with appropriate profiles (12 bis), or of a frame (37), or of rollers (12) whose rolling on the cams ensures non-slip contact. .
  • the invention indifferently uses tappets (33), latches (3), rockers (19-32), or rockers (20) to collect the reactions of the cams attacking the valves and also references (18) as shown in Figures (2), (3), when it comes to moving the camshaft away from the valves.
  • tappets 33
  • latches (3) rockers (19-32)
  • rockers 20
  • FIGS (2), (3) when it comes to moving the camshaft away from the valves.
  • Other advantages and embodiments of the invention will be described below, by way of nonlimiting examples, with reference to the appended drawings in les ⁇ uels:
  • - Figure (5) shows a main transverse view of a first embodiment of the invention.
  • - Figures (4) ⁇ (6) correspond respectively to the right and left views of this first embodiment of the invention.
  • - Figures (7) .. (8) show the adjustment roller and its axis of rotation equipped with an anti-wear pad.
  • FIG. (2) schematically represent two variants of the first embodiment of the invention in which the camshaft is located away from the valve by means of a return.
  • the return is placed upstream of the variation mechanism which retains its position at the top, near the valve.
  • FIG. 10 shows a main transverse view of a second embodiment of the invention.
  • - Figures (9), (II) correspond respectively to the right and left views of this second mode of the invention.
  • - Figure (I3) shows a main transverse view of a third embodiment of the invention.
  • - Figures (I2), (14) correspond respectively to the right and left views of this third embodiment of the invention.
  • - Figure (16) shows a main transverse view of a fourth embodiment of the invention.
  • - Figure (15) corresponds to the right view of this fourth mode of the invention, shown in section AA along the plane whose arrows
  • - Figure (17) corresponds to the top view of this fourth embodiment of the invention.
  • - Figures (18), (19), (20), (2l) schematically represent variants respectively of the first, second, third and fourth embodiment of the invention.
  • the cam (9) of the valve lift movement (6) is animated around the axis (14) an alternating oscillating movement, resulting from the transformation of the movement leading to rotation of the disc cam (10) and of the disc cam follower (il).
  • the roller (8) receives the lifting movement of the cam (9) and transmits it by its axis (13), to the latch (3) actuating the valve (6) .
  • the neutral part of the alternating cam (9) as well as the top of the latch (3) in contact with the axis (13) of the roller (8), are arcs of circles whose centers coincide with the axis (14) during the closing of the valve (6).
  • the U-shaped profile of the latch (3) provides lateral support for the roller (8).
  • the adjustment is made by positioning the roller (8) differently by a rotation around the axis (I4).
  • Each position of the roller (3) corresponds to a law of movement of the valve (6).
  • the support arms (15) of the axis (13) of the roller (8) are made integral by "bicycle" keys (16) to the control shaft (14).
  • the valve (6) is shown in the constantly closed position, but during the upward movement of the roller (8), the ends of the axis (13) describe the guide grooves machined in the arms (15), generally radially with respect to to the axis (l4).
  • the elements (13) and (3), in contact with each face of the shoe (17), have the same radius of curvature as the latter.
  • the shoe (17) therefore consists of two support faces in the form of arcs of circles around which two rotations are carried out simultaneously during the lifting of the valve (6); one in the gutter of the axis (13) and the other on the top of the latch (3).
  • the shoe (17) has a clearance necessary for the passage of the roller (8). This arrangement in the center provides lateral support for the shoe (17) by means of the roller (8).
  • Figures (9), (10), (II) show the second embodiment of the invention in which the cam (23) of the valve lifting movement (6) as well as its support latch (3) describe rotation around the axis (25) by actuating the valve (6).
  • the driving disc cam (10) attacks the tilting cam (23) with interposition of the balance (26).
  • the torsion spring (27) provides the stroke around the axis (14) of the balance (26) subject to the alternative primary movement.
  • the pendulum contacts (26) at each end are made by means of rollers; one (12) duc ⁇ tê of the driving disc cam (lO) and the other (22) on the side of the tilting cam (23).
  • the top of the support latch (3) has a circular arc profile concentric with that of the neutral part of the tilting cam (23) and the center of which coincides with the closing of the valve (6) with the axis d 'oscillation (14) of the balance (26).
  • the adjustment is made by positioning the tilting cam (23) differently by rotation on the top of the support latch (3) with the control shaft (25) by means of meshing teeth.
  • This type of connection does not introduce any relative movement of the tilting cam (23) on the support latch (3) during the lifting of the valve (6).
  • the support latch (3) comprises, on the side of the oscillation axis (25), a yoke which laterally guides the tilting cam (23) whose width is constant.
  • the part of the tilting cam (23) going into the above-mentioned yoke also has a constant thickness. Sn effect, the back and the top of the tilting cam (23) have arc profiles of concentric circles.
  • the transverse axis (24) located at the end of the yoke maintains the tilting cam (23) on the support latch (3) 0
  • the top, the neutral part and the back of the tilting cam (23) in contact with the top of the support latch (3) are rectilinear.
  • the roller (22) attacks the tilting cam (23) in the rectilinear direction as the neutral part of the cam tilts lante (23) gives when the valve (6) is closed.
  • the disc cam (10) ensures the reciprocating rectilinear movement of the roller (22) and the coil spring (21), the return.
  • the static cam (31) of the secondary movement of valve lift (6), as well as the top of the latch (3), are traversed by the roller (28-29).
  • the roller (28-29) is animated by the balance (30) of the alternating primary oscillating movement, around the axis (l4) j communicated by the disc cam (io) and the disc cam follower (il) .
  • the ends of its axis (13) describe the guide grooves machined in the balance (30), generally radially with respect to the axis (14).
  • Each end of the axis (13) has a flat which limits the stresses at the level of contact with the aforementioned grooves and ensures the lateral of the axis (13)
  • the neutral part of the static cam (3l) and the top of the latch (3) are arcs of circles whose centers coincide with the axis of oscillation (14) during the closing of the valve (6).
  • a "bicycle" key (16) makes the static cam (31) integral with the oscillation shaft (14).
  • the adjustment is made with the control shaft (14), by positioning the static cam (3l) differently by rotation. At each position, the static cam (3l) corresponds to a law of movement of the valve (6).
  • a roller (28-29) of monolithic design is incompatible with the good resistance of the surface conditions due to the slippage resulting from the simultaneous compression contacts between the static cam (31) and the latch (3).
  • the roller (28-29) consists of three rolling elements; the central roller (29) runs only through the latch (3) and the two identical end rollers (28) roll on the static cam (3l).
  • the central roller (29) has a diameter greater than the rollers (28) so as to prevent any contact of the rollers (28) with the latch (3).
  • the always delicate lateral positioning of the latch (3) does not therefore require any particular precaution.
  • the static cam (31) has a central clearance necessary for the passage of the roller (29).
  • the reciprocating rectilinear movement is communicated to the roller (28-29) by the guide element (30) driven by the disc cam (10) and the return spring (2l).
  • the neutral part of the static cam (3l) and the top of the Mnguet (3) are therefore rectilinear and parallel during the closing of the valve (6).
  • the adjustment is made by moving the static cam (31) in this rectilinear direction.
  • Figures (15), (16), (17) show the fourth embodiment of the invention, the method of variation of which consists in shifting the alternating movement of the cam (9), by means of a planetary gear train .
  • the alternating cam (9) drives the roller (33) of the rocker (32) actuating the valve (6). It is obvious that the roles played by the alternative cam (9) and the contact roller (33) can be reversed. In this case the cam then tilting, machined in the rear part of the rocker (32), is attacked by a roller driven by the same alternating oscillating movement around the axis (l4), as the cam (9). In the assembly of the planetary gear train shown here, the control is done by the central pinion cut in the shaft (14), around which the carrier train (9) and the outer sector (34) bones.
  • the external sector (34) receives the alternating primary movement of the disc cam (10) and of the disc cam follower (il) by the contact of the two rollers (12), and communicates it to the intermediate satellites (35) integral with the alternative cam (9) which acts as a train carrier.
  • the satellites (35) mesh with the control shaft (14) which remains stationary and around which the reciprocating oscillating movement is communicated to the carrier cam (9) .
  • a rotation of the control shaft (14) corresponds to an additional rotation of the satellites (35), which offsets the undercarriage cam (9) relative to the oscillating sector (34) and to the roller in contact (33).
  • each position of the control shaft (14) corresponds to a different lifting law of the valve (6).
  • the properties of planetary gears allow indifferently to adopt the external sector (34), the train carrier (9), the central pinion of the shaft (14), as control or entry or exit, according to six possibilities gathered on the table Ci below in which the following notations designate:
  • SE external sector
  • PT train carrier
  • PC central pinion
  • the first line of this table corresponds to the embodiment shown in Figures (15), (16), (17).
  • the movements of the undercarriage cam (9) and of the rack (34) are alternating rectilinear.
  • the disc cam (10) and the disc cam follower (it) communicate via the frame (37), the movement, alternating primary rectilinear the rack (34).
  • the adjustment is made by moving the control rack (14) which, via the satellite (35), shifts the train carrier cam (9).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Transmission Devices (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP83900048A 1981-12-31 1982-12-29 Verstellbare ventilsteuerung einer viertakt-brennkraftmaschine Expired EP0097665B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8124559A FR2519375B1 (fr) 1981-12-31 1981-12-31 Distribution variable pour moteur a quatre temps
FR8124559 1981-12-31

Publications (2)

Publication Number Publication Date
EP0097665A1 true EP0097665A1 (de) 1984-01-11
EP0097665B1 EP0097665B1 (de) 1986-11-12

Family

ID=9265558

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83900048A Expired EP0097665B1 (de) 1981-12-31 1982-12-29 Verstellbare ventilsteuerung einer viertakt-brennkraftmaschine

Country Status (6)

Country Link
US (1) US4572118A (de)
EP (1) EP0097665B1 (de)
JP (1) JPS59500002A (de)
DE (1) DE3274277D1 (de)
FR (1) FR2519375B1 (de)
WO (1) WO1983002301A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005090757A1 (de) * 2004-02-20 2005-09-29 Bayerische Motoren Werke Aktiengesellschaft Hubvariabler ventiltrieb für eine brennkraftmaschine

Families Citing this family (84)

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Publication number Priority date Publication date Assignee Title
FR2570123B1 (fr) * 1984-09-11 1988-11-18 Peugeot Dispositif de commande variable d'une soupape a tige pour moteur a combustion interne
US4770060A (en) * 1986-02-19 1988-09-13 Clemson University Apparatus and method for variable valve timing
US4771742A (en) * 1986-02-19 1988-09-20 Clemson University Method for continuous camlobe phasing
GB8723256D0 (en) * 1987-10-03 1987-11-04 Jaguar Cars Valve mechanisms
US4836155A (en) * 1988-01-11 1989-06-06 Slagley Michael W Variable duration valve opening mechanism
IT1220275B (it) * 1988-01-19 1990-06-15 Franco Storchi Complesso di elementi per la fasatura variabile delle valvole di un motore,in particolare di un motore a combustione interna
GB2214570A (en) * 1988-01-22 1989-09-06 Ford Motor Co Variable lift i.c. engine valves
DE3833540A1 (de) * 1988-10-01 1990-04-12 Peter Prof Dr Ing Kuhn Vorrichtung zur betaetigung der ventile an verbrennungsmotoren mit veraenderlicher ventilerhebungskurve
US5020488A (en) * 1989-11-22 1991-06-04 Fuji Jukogyo Kabushiki Kaisha Valve mechanism for an internal combustion engine
US5184401A (en) * 1990-11-30 1993-02-09 Mazda Motor Corporation Method of assembling valve drive mechanism to engine
US5165370A (en) * 1991-04-25 1992-11-24 Gerald Beaumont Mechanism for controlling valve timing
JP2944264B2 (ja) * 1991-07-23 1999-08-30 株式会社ユニシアジェックス 内燃機関の動弁装置
DE4135257C2 (de) * 1991-10-25 1998-09-03 Peter Prof Dr Ing Kuhn Vorrichtung zur Betätigung der Ventile in Verbrennungsmotoren mittels umlaufender Nocken
WO1993008377A1 (de) * 1991-10-25 1993-04-29 Peter Kuhn Vorrichtung zur betätigung der ventile in verbrennungsmotoren mittels umlaufender nocken
DE4223173A1 (de) * 1992-07-15 1994-01-20 Bayerische Motoren Werke Ag Ventiltrieb einer Brennkraftmaschine
US5732669A (en) * 1992-12-13 1998-03-31 Bayerische Motoren Werke Aktiengesellschaft Valve control for an internal combustion engine
DE4242634C2 (de) * 1992-12-17 1998-02-05 Uwe Dipl Ing Kirchner Einrichtung zur stufenlosen Variierung von Ventilhub und Steuerzeiten der Einlaß- und der Auslaßventile einer Hubkolbenbrennkraftmaschine
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
EP0638706A1 (de) * 1993-08-05 1995-02-15 Bayerische Motoren Werke Aktiengesellschaft Ventiltrieb einer Brennkraftmaschine
US5463987A (en) * 1994-07-13 1995-11-07 Cukovich; Mark S. Variable valve timing mechanism
DE19640520A1 (de) * 1996-07-20 1998-04-09 Dieter Dipl Ing Reitz Ventiltrieb und Zylinderkopf einer Brennkraftmaschine
US6016779A (en) * 1996-09-02 2000-01-25 Honda Giken Kogyo Kabushiki Kaisha Valve operating system in internal combustion engine
US20030159667A1 (en) * 1997-02-13 2003-08-28 Armstrong Mark Frederick Adjustment mechanism for valves
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FR2519375A1 (fr) 1983-07-08
WO1983002301A1 (en) 1983-07-07
DE3274277D1 (en) 1987-01-02
FR2519375B1 (fr) 1986-07-11
EP0097665B1 (de) 1986-11-12
US4572118A (en) 1986-02-25
JPS59500002A (ja) 1984-01-05

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