EP0155434A1 - Mécanisme de commande de soupapes avec réglage de jeu automatique pour moteur à combustion - Google Patents

Mécanisme de commande de soupapes avec réglage de jeu automatique pour moteur à combustion Download PDF

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Publication number
EP0155434A1
EP0155434A1 EP84810362A EP84810362A EP0155434A1 EP 0155434 A1 EP0155434 A1 EP 0155434A1 EP 84810362 A EP84810362 A EP 84810362A EP 84810362 A EP84810362 A EP 84810362A EP 0155434 A1 EP0155434 A1 EP 0155434A1
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EP
European Patent Office
Prior art keywords
valve
cam
wedge
grooved
adjusting wedge
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Withdrawn
Application number
EP84810362A
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German (de)
English (en)
Inventor
Willy Ernst Salzmann
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 EP0155434A1 publication Critical patent/EP0155434A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • 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

Definitions

  • the present valve train comprises an automatic backlash adjustment in particular according to claim 4, a device for adjusting the valve times and the valve lift according to claim 10 and the cylinder heads matching this valve train according to claim 12.
  • the automatic game adjustment is simple, has low moving masses and low elasticity and does not require any additional space compared to manual control. This means that it can be used cost-effectively with any valve train. It replaces the time-consuming adjustment of the valve clearance during initial assembly and revision of the engine, as well as periodic checking and adjustment during operation, and ensures that the valves always run with almost no play. This ensures constant valve times (very important for consumption and pollutants) and prevents annoying valve noises and unnecessary wear, protects the valve seats at risk from unleaded petrol and eliminates any risk of burned valves due to lack of play.
  • This mechanical backlash setting is considerably more compact, lighter and cheaper than the known hydraulic systems, has less friction on the cam base circle and enables "sharper" cams or higher speeds as well as more precise, noiseless valve closing. Their application is intended and sensible for all common valve train of two and four stroke engines.
  • FIG. 1 shows a variant of FIG. 1
  • FIG. 6 shows variants of FIG. 5.
  • FIG. 7 shows a variant of FIG. 6 in cross section through the cylinder head, while FIGS. 8, 9 and 10 each represent further variants in half cross section.
  • the usual valve springs, spring plates and half cones are omitted for simplification.
  • the camshaft 1 is of conventional design, as is the base circle 2 of the cam 3. According to the invention, however, the sliding surface of the cam flanks 4 and the cam tip 5 has fine tangential grooves 6, each in a normal plane to the neck shaft axis 10 lie and engage in such grooves 6 'of a wedge-shaped slider 7 ("adjusting wedge").
  • the adjusting wedge 7 is guided displaceably parallel to the camshaft axis 10 on a sliding surface 8 of the cup tappet 9 which is inclined at the same angle and is set against the cam 3 by a soft, spiral spring 11 (to the right in FIG. 1).
  • the spring 11 has one or more turns and an angled end 11 'which engages through a slot 12 (Fig.
  • the bucket tappet 9 carries a e.g. made of square wire curved sliding block 14, which runs in a groove of the ram guide (Fig. 10).
  • the mode of operation is as follows: during at least half a camshaft revolution, the smoothly ground base circle 2 of the neck 3 runs on the adjusting wedge 7, which, because its grooves 6 'cannot be held on the non-grooved cam surface 2, automatically shifts such that valve clearance is set to zero becomes. This displacement takes place either under the action 7 * of the soft spring 11 in FIG. 1 to the right (play reduction) or under the action 13 * of the valve spring and the inclined sliding surface 8 to the left (play increase). As soon as a cam flank 4 comes into play, the adjusting wedge 7 has a tendency to move to the left until its grooves 6 '' engage 'in the grooves 6 of the cam flanks 4 and run there until the valve closes, etc.
  • Fig. 4 shows the profile of the grooves 6 and 6 'of Fig. 1 in a large magnification.
  • 6 a are symmetrical, 6 b asymmetrical, rounded serrations and 6 c a sinus profile in the engaged state of parts 4/5 and 7.
  • the grooves 6/6 ' can be adjusted to their full width simultaneously by turning, milling, profile rolling and / or grinding of the cam 3 or the wedge 7 generate.
  • the cam base circle 2 is ground beforehand or subsequently smooth, with a smooth transition into the tip 6 * or better into the bottom 6 ** of the grooves 6 of the cam flanks 4.
  • the basic shape of the adjusting wedge 7 (FIG. 1) is eventual. together with the grooves 6 ', for example by rolling, extrusion or sintering (for example hard metal).
  • a variant is an un-grooved, but e.g. provided with soft material (aluminum, tin, Teflon, etc.) coated surface of the adjusting wedge 7, into which the grooves 6 'run.
  • Soft material aluminum, tin, Teflon, etc.
  • cam flanks 4 and cam tips 5 are also conceivable, which instead of the grooves 6 e.g. only have scoring marks, which can have a light, helical shape; the base circle 2 can have an opposite tightening (counter screw) in an analogous manner.
  • the entire sliding surface (lateral surface) 20 of the cam 21 is conical at a constant angle, as a result of which the sliding surface 22 of the plunger 9 ′ lies in a normal plane to the plunger axis and the forces 15 ′ and 15 ′′ of FIG. 1 do not occur
  • the adjusting wedge 7 can be fixed or in one piece with the tappet 9 'and follow the cam which can be displaced on a cylindrical, ground camshaft and which is driven, for example, by a wedge, the spiral spring 11 being replaced by a helical spring 23.
  • the sliding surface 22 can be grooved and the plunger 9 'can be inclined by the cone angle of the displaceable cam, the grooves 6 of the cam having to be machined at this angle 13' Even greater inclination of the valves is possible by inclining the grooved surface 22, but this leads to cranked cams rt.
  • FIG. 6 shows in cross section a conical cam 24 analogous to FIG. 5, which actuates the valve 13 via a rocker arm 25.
  • the rocker arm 25 carries in a dovetail groove parallel to the camshaft axis 10 a wide adjusting wedge 26, the ball 27 of which is grooved exactly to the cam 24 and is set by a bow or hairpin spring 28.
  • the bale 27 can be replaced by a conical, grooved roller 29 which moves on its axis by a spring.
  • the rocker arm is not articulated on the axis 33 but, for example, on a ball pin and is guided laterally on the valve stem 13 in a known manner.
  • the bale 27 is a fixed part of the rocker arm 25 and the cams 24 the camshaft against a spring 23 (Fig. 5).
  • the rocking lever 25, with the ball 27 fixed thereon moves on its axis of rotation 30 against the fixed, conical cam 24; a small coil spring on the axis 30 as an adjusting spring is the only additional part of this automatic play adjustment compared to a manual one.
  • FIG. 6 also shows a device which presupposes and expediently supplements an automatic play adjustment and which serves to adjust the valve times and the valve lift.
  • This is done in a relatively simple manner in that the axis of rotation 30 of the rocking lever 25 is displaced in the direction of the valve 13 (position 30 '), which is done, for example, by an actuating shaft 31 with levers 32 fixed thereon.
  • a cam track 33 of the rocker arm, which actuates the valve 13 via a non-rotating, curved valve cap 34, is shaped in such a way that with this shift from 30 to 30 'the valve clearance remains at least approximately constant.
  • the cam track 33 generates lateral forces on the valve 13 and requires particularly long valve guides or, for example, a valve cap with tappet segments 35 or event. an appropriately trained valve plate.
  • the setting shaft 31 can be rotated, for example, by intake manifold vacuum or steplessly by a map-controlled servo motor and, in FIG. 6, in the direction of rotation 36 of the camshaft 37, the inlet control is pre-adjusted by approx %. This can significantly reduce consumption and NS x formation at part load.
  • the present concept allows the intake and exhaust valves 13 to be adjusted independently of one another when they are driven by a single camshaft 37 by two actuating shafts 31 which are arranged on one side or (symmetrically) on both sides of the valves 13. 7, the actuating shaft (s) 31 can be mounted in the simplest manner in the flange 82 of a cylinder head cover similar to 50, into which the camshaft 37 with its bearing disks 38 is inserted.
  • rocker arms 25 are provided, which have a ball joint instead of the axis of rotation 30, moreover event.
  • the levers 32 which are subjected to pressure and tension can be replaced by a hydraulic cylinder which is prestressed under pressure, as a result of which 25 and 26 become one piece and the cam 24 is not grooved.
  • Fig. 7 shows in cross section the simple and compact valve train of an engine with two or four valves 13 per cylinder, which are arranged in pairs (one intake and one exhaust valve) at a small angle (e.g. 10 °) to each other and by two the same angle lever 40 can be actuated by a common, cylindrical cam 41.
  • the grooves of the cylindrical balls 42 of the adjusting wedges 43 engage from both sides in the grooves of the cam 41, which requires a symmetrical groove profile (for example 6 a or 6 c in FIG. 4) and makes full use of these grooves, but an exact longitudinal guidance of the central one Requires camshaft 44.
  • the cranked hubs 45 of the angle levers 40 are also guided axially against one another and on the bearing and lubrication tube 46.
  • the game setting takes place here also by the bow or hairpin springs 47 or the like. through the valve springs, as explained in FIGS. 1 to 3.
  • the cross-flow cylinder head 48 shown on the right in partial half-section in FIG. 7 is as narrow as the cylinder, which allows inexpensive, short intake and exhaust manifolds.
  • valve train is self-adjusting and completely maintenance-free, it does not need to be accessible even during assembly.
  • the cylinder head 48 can be closed with a single, compact cover 50 which supports the inserted camshaft 44 on disks 51 'and fixes the bearing tube 46 of the angle lever 40.
  • the entire assembly is carried out without further parts and exclusively by means of the usual cylinder head stud bolts 52, which are arranged at approximately the same distance from one another, which saves around 10 to 20 screw connections in a four-cylinder in-line engine compared to today.
  • a valve train of which FIG. 8 shows a partial half cross section, is even simpler and more compact.
  • a central camshaft 55 actuates two parallel intake or exhaust valves, each preferably conical cam 56 acting on a crossbar 58 via an adjusting wedge 57.
  • This crossbeam 58 is fixedly connected to two cup tappets 59, preferably drawn from sheet metal, at least in the middle 60 thereof (eg by spot welding). Rough differences in height of the valves 13 can be compensated for with sliding pieces 57 and / or valve caps 61 of different thicknesses.
  • This very simple valve train with four parallel valves 13 per cylinder fits, for example, a diesel with direct injection or a DC flushed two-stroke engine.
  • cams Shaft 55 lies in the upper flange plane 62 of a very narrow cylinder head, its usual separate bearing covers are replaced by a cover approximately according to 66 of FIG. 9, which is exclusively fastened by the cylinder head screws 67.
  • a camshaft bearing according to FIG. 7 with a cover approximately according to 50 is also possible. 66 possibly made of sheet metal.
  • FIGS. 9 shows in half cross section through a bearing of the camshaft 1 the upper part of the cylinder head 65 and the cylinder head cover 66 of a valve train according to FIGS. 1 and 2.
  • This head is extremely narrow because the cylinder head screws 67 have smaller distances 68 than usual (FIG 7) what is conceivable because of the long expansion screws 67.
  • their longitudinal axes 69 can be inclined relative to one another in accordance with 69 ′ in order to uniformly load the cylinder head gasket as usual and still maintain the narrow, dull cover 66.
  • the bearing bores 70 for the camshaft 1 are preferably cleared and save the usual, separate camshaft bearing caps with two screws each.
  • Fig. 10 shows the same valve train, but in a V-arrangement (e.g. 30 °) with two or four valves per cylinder and central spark plug.
  • the cylinder head 75 is wider at the top, but the same covers 66 (FIG. 9) can be used (kit). However, they can only be fastened on the inside by the cylinder head screws 67; on the outside, additional, smaller screws 76 are required.
  • the flange 77 of the cover 66 must be inclined at a double angle.
  • the oil supply to the cam 3 takes place through the bores 78 and 79, the adjusting wedges 7 have lubrication grooves 80 and / or e.g. PFTE-coated sliding surfaces or linear needle bearings.
  • valve drives with lateral camshafts and rocker arms and possibly tappets and push rods are also provided.
  • Fig. 1, 2 and 5 can be turned upside down and the cup tappets 9 and 9 'replaced by barrel or mushroom tappets, which are to be adjusted by additional springs, so that the adjusting wedge 7 can be moved freely after the valve closes.
  • Fig. 6 with wedge 26 respectively.
  • These valve drives also have the simplest cylinder heads analogous to FIG. 7, but with rocker arms on the bearing tube 46 and flat cover 81. However, existing, conventional cylinder heads can also be used in all examples.
EP84810362A 1984-02-20 1984-07-23 Mécanisme de commande de soupapes avec réglage de jeu automatique pour moteur à combustion Withdrawn EP0155434A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH79584 1984-02-20
CH795/84 1984-02-20

Publications (1)

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EP0155434A1 true EP0155434A1 (fr) 1985-09-25

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EP84810362A Withdrawn EP0155434A1 (fr) 1984-02-20 1984-07-23 Mécanisme de commande de soupapes avec réglage de jeu automatique pour moteur à combustion

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6552110B1 (en) * 1997-10-21 2003-04-22 Dow Global Technologies Inc. Thermoplastic marking compositions
DE10164493B4 (de) * 2001-12-29 2010-04-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung zur variablen Betätigung der Ladungswechselventile in Hubkolbenmotoren

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1609711A (en) * 1926-04-26 1926-12-07 William M Goodwin Valve-operating mechanism for internal-combustion engines
US2222138A (en) * 1938-02-28 1940-11-19 Thompson Prod Inc Mechanical clearance regulator
US2694389A (en) * 1952-10-14 1954-11-16 Eaton Mfg Co Valve gear length adjusting mechanism
US2970583A (en) * 1959-07-27 1961-02-07 Ford Motor Co Valve gear
US3118322A (en) * 1964-01-21 Figure
GB2056011A (en) * 1979-08-10 1981-03-11 Daimler Benz Ag Valve-clearance compensating means for an internal combustion engine
GB2062158A (en) * 1979-10-26 1981-05-20 Daimler Benz Ag Mechanical valve clearance compensating device
US4512953A (en) * 1981-05-25 1985-04-23 Avl Ag Analyzing apparatus for the analysis of liquid samples

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118322A (en) * 1964-01-21 Figure
US1609711A (en) * 1926-04-26 1926-12-07 William M Goodwin Valve-operating mechanism for internal-combustion engines
US2222138A (en) * 1938-02-28 1940-11-19 Thompson Prod Inc Mechanical clearance regulator
US2694389A (en) * 1952-10-14 1954-11-16 Eaton Mfg Co Valve gear length adjusting mechanism
US2970583A (en) * 1959-07-27 1961-02-07 Ford Motor Co Valve gear
GB2056011A (en) * 1979-08-10 1981-03-11 Daimler Benz Ag Valve-clearance compensating means for an internal combustion engine
GB2062158A (en) * 1979-10-26 1981-05-20 Daimler Benz Ag Mechanical valve clearance compensating device
US4512953A (en) * 1981-05-25 1985-04-23 Avl Ag Analyzing apparatus for the analysis of liquid samples

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6552110B1 (en) * 1997-10-21 2003-04-22 Dow Global Technologies Inc. Thermoplastic marking compositions
DE10164493B4 (de) * 2001-12-29 2010-04-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung zur variablen Betätigung der Ladungswechselventile in Hubkolbenmotoren

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