EP3268597B1 - Moteur a combustion interne pourvu d'au moins un cylindre - Google Patents

Moteur a combustion interne pourvu d'au moins un cylindre Download PDF

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Publication number
EP3268597B1
EP3268597B1 EP16713721.5A EP16713721A EP3268597B1 EP 3268597 B1 EP3268597 B1 EP 3268597B1 EP 16713721 A EP16713721 A EP 16713721A EP 3268597 B1 EP3268597 B1 EP 3268597B1
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EP
European Patent Office
Prior art keywords
cylinder
cylinder head
plane
internal combustion
valve
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EP16713721.5A
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German (de)
English (en)
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EP3268597A1 (fr
Inventor
Andreas Zurk
Manfred Breitenberger
Günter Häusl
Martin KLAMPFER
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AVL List GmbH
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AVL List GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0004—Crankcases of one-cylinder engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0007—Crankcases of engines with cylinders in line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings
    • F02F2007/0063—Head bolts; Arrangements of cylinder head bolts

Definitions

  • the invention relates to an internal combustion engine with at least one cylinder with at least one cylinder head connected to a cylinder housing via several cylinder head bolts per cylinder, two inlet valves and two outlet valves being arranged per cylinder, which have a twisted valve pattern in relation to a longitudinal plane of the engine, with each exhaust valve an outlet sub-duct is guided and an inlet sub-duct leads to each inlet valve, the screw axes of all cylinder head screws assigned to a cylinder spanning cylinder head screw planes arranged parallel to the cylinder axis, all cylinder head screw planes being inclined both to the engine longitudinal plane and to an engine transverse plane normal to the engine longitudinal plane are.
  • the pamphlet DE 43 43 556 A1 describes an internal combustion engine with two inlet valves and two outlet valves per cylinder and a twisted valve pattern, all cylinder head screw planes assigned to a cylinder being inclined both to the engine longitudinal plane and to the engine transverse plane.
  • a similar internal combustion engine is in the DE 18 00 774 A1 shown.
  • JP S58 180359 U discloses an internal combustion engine with four gas exchange valves per cylinder, the valve pattern not being rotated and cylinder head screws arranged in the form of a hexagon being assigned to each cylinder.
  • a partial outlet channel is routed from each outlet channel and a partial inlet channel is routed to each inlet valve.
  • the outlet sub-channels and the inlet sub-channels unite within the cylinder bore diameter to form a common outlet channel or a common inlet channel.
  • the JP S60 162241 U discloses an internal combustion engine with four valves per cylinder that are rotated.
  • the cylinder head bolts which are arranged in the form of a hexagon, span planes that are both inclined to the longitudinal plane of the engine and inclined to the transverse plane of the engine.
  • the object of the invention is to avoid these disadvantages and to create a compact, structurally rigid internal combustion engine with a simple valve drive which allows the greatest possible flexibility in the positioning of components with little effort.
  • this is achieved in that the partial outlet channels unite outside a cylinder bore diameter to form a common outlet channel and / or a common inlet channel is divided into the partial inlet channels in the area of a cylinder bore diameter, the area of a triangle consisting of a projection of the inlet valve axes and an inlet channel separation point and / or the exhaust valve axis and an exhaust port connection point in the plane in or parallel to a cylinder head gasket plane is between 5 percent and 15 percent of the bore area.
  • the area of the triangle is preferably 7 percent of the bore area. In this way, in particular, favorable cylinder head rigidity can be achieved.
  • the cylinder head screw arrangement is thus rotated about the cylinder axis.
  • Variants of the invention are implemented, for example, in single cylinder heads and / or in internal combustion engines with one or more cylinders, the cylinder heads of which are fixed with four cylinder head screws.
  • the engine longitudinal plane is spanned by the crank axis of the crankshaft of the internal combustion engine and at least one cylinder axis of a cylinder.
  • Motor transverse planes are understood here to mean normal planes on the longitudinal plane of the motor, which run through the cylinder axis or parallel to it.
  • the valve pattern is to be understood here as the arrangement of the inlet and outlet valves viewed in the outline of a cylinder.
  • a twisted valve pattern is a valve pattern in which the valve symmetry plane with the longitudinal plane of the engine includes an angle of rotation not equal to 0 ° (also not equal to 90 °, 180 ° and 270 °), the valve symmetry plane through the cylinder axis or parallel to the cylinder axis and through runs the midpoint of the distance between the inlet valves and the midpoint of the distance between the outlet valves.
  • the angle of rotation of the valve pattern ⁇ is between 35 ° and 50 °, preferably 45 °. This allows a favorable configuration of channel courses, valve train positioning and generally for packaging to be achieved.
  • the screw pattern can have the shape of a polygon, for example a square - in particular a rectangle or a square.
  • the screw pattern of the cylinder head screws of at least one cylinder is favorably rotated with respect to the cylinder axis.
  • the screw pattern of the cylinder head screws is understood here to mean the arrangement of the screw axes of the cylinder head screws viewed in the outline of a cylinder. In the case described here, said screw axes lie at the corner points of a polygon.
  • a screw pattern rotated in relation to the cylinder axis is to be understood here as a screw pattern in which all cylinder head screw planes defined by two adjacent or, for example, diametrically opposite cylinder head screws (the respective cylinder head screw plane is therefore spanned by the screw axis of the associated cylinder head screws) of two cylinder head screws of a cylinder - in Viewed from the floor plan - are inclined or rotated to the engine longitudinal plane and / or to the engine transverse plane.
  • each cylinder head screw plane assigned to a cylinder includes a screw plane angle other than zero with the longitudinal axis of the engine.
  • the angle of rotation of the screw pattern can be defined, for example, by the smallest of all screw plane angles assigned to a cylinder. It is particularly advantageous if the angle of rotation of the screw pattern is between approximately 5 ° and 45 °, preferably between approximately 15 ° and 30 °, for example 23 °.
  • the absolute amounts of the angle of rotation of the screw pattern and the angle of rotation of the valve pattern are designed to be the same.
  • the inlet and outlet valves, including the bolt pattern of the cylinder head bolts are twisted around the cylinder axis by the same angle - either oriented the same or opposite -.
  • the angle of rotation of the valve pattern is defined as the angle between a valve symmetry plane running between two inlet valves on the one hand and two outlet valves on the other hand and a longitudinal plane of the engine.
  • At least one cylinder head screw of a first cylinder head and at least one cylinder head screw of a second cylinder head of adjacent cylinders in the area of at least one between the adjacent cylinders Engine transverse plane are arranged.
  • the images of the cylinder head bolts preferably overlap or overlap in a parallel projection onto the longitudinal plane of the engine.
  • the cylinder head screws are usually arranged in the area of tab-like projections of the cylinder head, which projections increase the space requirement of the cylinder head.
  • the cylinder head generally has a smaller radial extent between two projections. The required installation space can be significantly reduced if a projection of a cylinder head of an adjacent cylinder is positioned between two adjacent projections of a cylinder.
  • the angle ⁇ 1 between the inlet valve symmetry plane and the engine longitudinal plane and / or the angle ⁇ 2 between the exhaust valve symmetry plane and the engine longitudinal plane is between 35 ° and 50 °, preferably 45 °.
  • the angle ⁇ 1 between the inlet valve symmetry plane and the engine longitudinal plane and / or the angle ⁇ 2 between the exhaust valve symmetry plane and the engine longitudinal plane are identical to the rotation angle ⁇ of the valve image.
  • Fig. 1 shows a plan view of a cylinder head 11 of an internal combustion engine 2 according to the invention.
  • the solution shown is particularly advantageous for Internal combustion engines with internal cylinder pressures of approx. 200 bar and above.
  • Two inlet valves 3, 4 and two outlet valves 5, 6 are provided for each cylinder 1.
  • the cylinder axis 1a runs vertically to the image plane.
  • the inlet valves 3, 4 have a flow through a common inlet channel 7, the inlet channel 7 dividing in the direction of the cylinder axis 1a approximately in the area of the cylinder bore diameter - indicated by the circle 8 - into partial inlet channels 7a, 7b each leading to one inlet valve 3, 4.
  • an inlet duct separation point 30 is shown: This is a projection of the duct courses in a plane in or parallel to a cylinder head sealing plane (corresponds to FIG Fig. 4 the plane of the sheet) around that point in the separation area of the partial inlet channels 7a, 7b, which is closest to the cylinder axis 1a.
  • the separation area means here that no precise separation point can be defined due to the cross-sectional shape of the channels.
  • Fig. 4 also shows the inlet valve axes 3a, 4a which are normal to the plane of the sheet of FIG Fig. 4 run and at the same time form the centers of the respective valve openings.
  • FIG. 4 An outlet duct connection point 31 can be seen: This is a projection of the duct courses in a plane in or parallel to a cylinder head sealing plane (corresponds to FIG Fig. 4 the plane of the sheet) around that point of the connecting area of the partial outlet channels 9a, 9b which is closest to the cylinder axis 1a.
  • the term connecting area also takes into account the cross-sectional convergence of the partial outlet channels 9a, 9b.
  • Fig. 4 also shows the outlet valve axes 5a, 6a, which are normal to the plane of the sheet of FIG Fig. 4 run and at the same time form the centers of the respective valve openings.
  • Inlet channel 7 and outlet channel 9 lead to an inlet flange 7c and outlet flange 9c, respectively.
  • partial inlet channels 7a, 7b or the partial outlet channels 9a, 9b are not brought together, but instead lead to their own partial inlet flanges and partial outlet flanges.
  • valve drive of a known type via valve bridges 10a, 10b connecting the inlet 3, 4 and outlet valves 5, 6, which are mounted via valve spring assemblies 14 and one mounted on a rocker arm shaft 12
  • Rocker arm arrangement 13 - namely an inlet rocker arm 13a and an outlet rocker arm 13b - can be actuated via push rods 15a, 15b.
  • a rotated valve pattern is implemented. This means that the positions of the inlet 3, 4 and outlet valves 5, 6 or the associated openings are rotated clockwise or counterclockwise about the cylinder axis 1a.
  • a valve pattern in which the valve plane of symmetry 17 and the engine longitudinal plane 2a includes a rotation angle ⁇ ⁇ 0 is referred to as a twisted valve pattern.
  • the valve symmetry plane 17 is a plane running normal to the plane of the drawing or to the cylinder head sealing surface that coincides with the plane of the drawing through the center point 17a of the distance between the inlet valves 3, 4 and the center point 17b of the distance between the outlet valves 5, 6.
  • valve symmetry plane 17 Compared to a conventional tandem valve pattern, where the valve symmetry plane 17 runs parallel to or coincides with the engine longitudinal plane 2a, the valve symmetry plane 17 is inclined at an angle ⁇ of approx. 35 ° -45 ° relative to the engine longitudinal plane 2a in the illustrated embodiment .
  • the ramifications of the partial inlet channels 7a, 7b and partial outlet channels 9a, 9b run within the circle 8 representing the cylinder bore diameter at least approximately parallel or symmetrically to the valve plane of symmetry 17 of the inlet valves 3, 4 or outlet valves 5, 6.
  • the inlet valve symmetry plane 171 ( Fig. 4 ) runs normal to the image plane or to the cylinder head sealing surface coinciding with the image plane and normal to the connecting plane of the inlet valve axes 3a, 4a (this connecting plane runs through the two valve axes) through the center point 17a of the distance between the inlet valves 3, 4.
  • the angle ⁇ 1 between the Inlet valve symmetry plane 171 and the engine longitudinal plane 2a is between 15 ° and 85 °, preferably 45 ° - in this preferred variant it is thus identical to the angle ⁇ between valve symmetry plane 17 and engine longitudinal plane 2a.
  • the exhaust valve symmetry plane 172 also runs normal to the image plane or to the cylinder head sealing surface which coincides with the image plane and normal to the connecting plane of the exhaust valve axes 5a, 6a (this connecting plane runs through the two valve axes) through the center point 17b of the distance between the exhaust valves 3, 4
  • Angle ⁇ 2 between the exhaust valve plane of symmetry 172 and the engine longitudinal plane 2a is also between 15 ° and 85 °, preferably 45 ° - in this preferred variant it is thus identical to the angle ⁇ between the valve plane of symmetry 17 and the engine longitudinal plane 2a.
  • the partial inlet channels 7a, 7b and / or the partial outlet channels 9a, 9b thus run within the cylinder bore diameter parallel or symmetrically to the valve plane of symmetry 17 or to the inlet valve 171 or outlet valve plane of symmetry 172.
  • the projection of the inlet valve axes 3a, 4a and the inlet channel separation point 30 and / or the outlet valve axes 5a, 6a and the outlet channel connection point 31 into the plane in or parallel to the cylinder head gasket plane (corresponds in FIG Fig. 4
  • the triangle formed on the plane of the sheet has an area which corresponds to 5 to 15 percent, preferably 7 percent of the area of the hole. Bore area here denotes the area of circle 8, which denotes the cylinder bore diameter.
  • the triangle formed on the inlet side and outlet side can have the same, but also different surface areas within the specified limits.
  • the cylinder head screws 19, 20, 21, 22, indicated only by the screw holes, are arranged at the corner points of a polygonal cylinder head outer contour 23 of the cylinder head 11, in the illustrated embodiment a square, in the area of associated tab-like protrusions 25, 26, 27, 28.
  • the polygon can also be designed as a rectangle, hexagon or a different type of polygon.
  • the screw pattern of the cylinder head screws 19, 20, 21, 22, designed as a square in the exemplary embodiment is rotated about the cylinder axis 1a.
  • the twist angle ⁇ of the screw pattern is defined by the deviation from a conventional, untwisted screw pattern in which at least one cylinder head screw plane 24a, 24b, 24c, 24d, 24e, 24f is parallel to the engine longitudinal plane 2a or to the engine transverse plane 2b.
  • the angle of rotation ⁇ of the screw pattern is defined by the smallest of all screw plane angles assigned to a cylinder 1.
  • the angle of rotation ⁇ is defined by the screw plane angle between the two cylinder head screws which are opposite one another with regard to the cylinder axis 1a and are each closest to the engine longitudinal plane 2a. In the representation of Fig. 1 this would relate to the cylinder head screw 20 at the bottom left and the cylinder head screw 22 at the top right - "bottom left” and "top right” always with regard to the representation in FIG Fig. 1 .
  • a cylinder head screw radius 32 results for a circle running through the center points of all cylinder head screws 19, 20, 21, 22 (or their axes 19a, 20a, 21a, 22a) with the center point cylinder axis 1a.
  • this is cylinder head screw radius 32 between 60 percent and 95 percent, preferably 78 percent of the cylinder bore diameter 33 (that is to say the diameter of the circle 8).
  • the cylinder head screw spacing 34 between directly spaced cylinder head screws is then in the exemplary embodiment Fig. 1 and Fig. 5 with four cylinder head screws 19, 20, 21, 22 between 100 percent and 120 percent, preferably 111 percent of the cylinder bore diameter 33.
  • the cylinder head screw distance between spaced apart screws is between 70 percent and 90 percent, preferably 78 percent of the Cylinder bore diameter.
  • valve pattern and cylinder head screws are rotated by the same angle about the cylinder axis 1a, or by the same absolute amount, but in the opposite direction.
  • Fig. 6 shows such an embodiment, where the angle of the longitudinal axes of the inlet 13a and outlet rocker arms 13b is shown.
  • the angle ⁇ between the inlet rocker arm longitudinal axis 130a and the engine longitudinal plane 2a and the angle ⁇ between the outlet rocker arm axis 130b and the engine longitudinal plane 2a is between 65 ° and 115 °, preferably 80 °.
  • the angles can be the same, but also different within the specified ranges.
  • cooling jacket cores can be made with thicker walls, which leads to a higher coolant mass flow and correspondingly better cooling.
  • the additional space can also be used for the arrangement of measuring sensors.
  • FIG. 3 Another benefit is in Fig. 3 recognizable: Here a first 1 'and a second cylinder 1 "as well as a first and a second cylinder head 11', 11" of an internal combustion engine 2 according to the invention are shown, although further, adjacent cylinders can of course be present.
  • the cylinder heads 11 ', 11 are designed as individual cylinder heads in the example.
  • valve plane of symmetry 17 is rotated by an angle ⁇ of 35 ° -50 °, preferably 45 ° with respect to the longitudinal plane 2a of the engine, and when the cylinder head screw polygon is rotated by an angle of rotation ⁇ of 15 ° -35 °, is preferably rotated 25 ° relative to the engine longitudinal plane 2a.
  • merged channel branches also have the area of a triangle consisting of a projection of the inlet valve axes 3a, 4a and the inlet channel separation point 30 and / or the outlet valve axes 5a, 6a and the outlet channel connection point 31 into the plane in or parallel to the cylinder head sealing plane (corresponds to FIG Fig. 4 the sheet plane) between 5 percent and 15 percent, preferably 7 percent of the hole area.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (13)

  1. Moteur à combustion interne (2) ayant au moins un cylindre (1, 1', 1") avec au moins une tête de cylindre (11, 11', 11") reliée au corps de cylindre par plusieurs vis de tête de cylindre (19, 20, 21, 22, 19', 20', 21', 22', 19", 20", 21", 22"),
    - deux soupapes d'admission (3, 4) et deux soupapes d'échappement (5, 6) sont tournées par rapport au plan longitudinal (2a) du moteur, dont l'image de soupape est associée à chaque cylindre (1, 1', 1"),
    - un canal partiel d'échappement (9a, 9b) issu de chaque soupape d'échappement (5, 6) et un canal partiel d'admission (7a, 7b) rejoignant chaque soupape d'admission (3, 4),
    - les axes (19a, 20a, 21a, 22) de toutes les vis de tête de cylindre (19, 20, 21, 22, 19', 20', 21', 22', 19", 20", 21", 22") associées à un cylindre (1, 1', 1"), sous-tendent des plans de vis de tête de cylindre (24a, 24b, 24c, 24d, 24e, 24f) parallèles à l'axe de cylindre (1a),
    - tous les plans de vis de tête de cylindre (24a, 24b, 24c, 24d, 24e, 24f) associés à un cylindre (1, 1', 1") étant inclinés à la fois par rapport au plan longitudinal (2a) du moteur et à un plan transversal de moteur (2b, 2c) perpendiculaire au plan longitudinal (2a) du moteur,
    moteur à combustion interne caractérisé en ce que
    - les canaux partiels d'échappement (9a, 9b) se réunissant au-delà de l'alésage du cylindre en un canal d'échappement commun (9) et/ou un canal d'admission commun (7) se divise dans la zone de l'alésage de cylindre en canaux partiels d'admission (7a, 7b),
    - la surface du triangle composé de la projection des axes de soupape d'admission (3a, 4a) et du point de séparation du canal d'admission (30) et/ou des axes de soupape d'échappement (5a, 6a) et du point de jonction du canal d'échappement (31) dans le plan de la tête de culasse ou parallèlement à ce plan correspond à entre 5 pourcent et 15 pourcent de la surface d'alésage.
  2. Moteur à combustion interne (2) selon la revendication 1, caractérisé en ce que
    la surface du triangle représente 7 pourcent de la surface de l'alésage.
  3. Moteur à combustion interne (2) selon la revendication 1 ou 2,
    selon lequel
    l'image des vis de tête de culasse (19, 20, 21, 22, 19', 20', 21', 22', 19", 20", 21", 22") d'au moins un cylindre (11, 11', 11"), en vue en plan, a la forme d'un polygone,
    caractérisé en ce que
    l'image des vis de tête de culasse (19, 20, 21, 22, 19', 20', 21', 22', 19", 20", 21", 22") d'au moins un cylindre (1, 1', 1") est tournée par rapport à l'axe de cylindre (1a).
  4. Moteur à combustion interne (2) selon l'une des revendications 1 à 3,
    caractérisé en ce que
    chaque plan de vis de tête de cylindre (24a, 24b, 24c, 24d, 24e, 24f) associé à un cylindre (1, 1', 1") fait avec l'axe longitudinal (2a) du moteur un angle de plan de vis non nul.
  5. Moteur à combustion interne (2) selon l'une des revendications 1 à 4,
    caractérisé en ce que
    l'angle de pivotement (β) de l'image de vis est compris entre 5° et 45°, de préférence entre environ 15° et 30°.
  6. Moteur à combustion interne (2) selon la revendication 4 ou 5, caractérisé en ce que
    l'angle de pivotement (β) de l'image de vis est défini par le plus petit de tous les angles de plan de vis associés à un cylindre (1, 1', 1").
  7. Moteur à combustion interne (2) selon l'une des revendications 1 à 6,
    caractérisé en ce que
    l'angle de pivotement (β) de l'image de vis et l'angle de pivotement (α) de l'image de soupape sont identiques en valeur absolue.
  8. Moteur à combustion interne (2) selon l'une des revendications 1 à 7,
    comportant au moins deux têtes de cylindre (11', 11") réalisées comme tête de monocylindre pour deux cylindres voisins (1', 1"),
    moteur caractérisé en ce qu'
    au moins une vis de tête de cylindre (20') d'une première tête de cylindre (11') et au moins une vis de tête de cylindre (22") d'une seconde tête de cylindre (11") de cylindres voisins (1', 1") sont dans la zone d'au moins un plan transversal de moteur (2c) passant entre les cylindres voisins (1', 1").
  9. Moteur à combustion interne (2) selon la revendication 8, caractérisé en ce que
    les images des vis de tête de cylindre (20', 22"), en projection parallèle sur le plan longitudinal (2a) du moteur, se chevauchent ou se couvrent.
  10. Moteur à combustion interne (2) selon l'une des revendications 1 à 9,
    caractérisé en ce que
    chaque vis de tête de cylindre (19', 20', 21', 23', 19", 20", 21", 22") est prévue dans une excroissance en forme de patte (25', 26', 27', 28' ; 25", 26", 27", 28") de la tête de cylindre (11', 11") et entre deux excroissances voisines (26', 27' ; 25", 28") d'au moins une tête de cylindre (11', 11") il y a une excroissance (28", 26') d'une tête de cylindre (11', 11") voisine.
  11. Moteur à combustion interne (2) selon l'une des revendications 1 à 10,
    caractérisé en ce que
    l'angle de pivotement (a) de l'image de soupape est compris entre 35° et 50°, de préférence il est égal à 45°.
  12. Moteur à combustion interne (2) selon l'une des revendications 1 à 11,
    caractérisé en ce que
    l'angle (γ1) entre le plan de symétrie (171) de soupape d'admission et l'axe longitudinal du moteur (2a) et/ou l'angle (γ2) entre le plan de symétrie de soupape d'échappement (172) et le plan longitudinal du moteur (2a) est compris entre 35° et 50° et de préférence il est égal à 45°.
  13. Moteur à combustion interne (2) selon la revendication 12, caractérisé en ce que
    l'angle (γ1) entre le plan de symétrie de soupape d'admission (171) et le plan longitudinal du moteur (2a) et/ou l'angle (γ2) entre le plan de symétrie de soupape d'échappement (172) et le plan longitudinal du moteur (2a) sont identiques à l'angle de pivotement (a) de l'image de soupape.
EP16713721.5A 2015-03-13 2016-03-14 Moteur a combustion interne pourvu d'au moins un cylindre Active EP3268597B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50203/2015A AT516161B1 (de) 2015-03-13 2015-03-13 Brennkraftmaschine mit zumindest einem zylinder
PCT/AT2016/050059 WO2016145467A1 (fr) 2015-03-13 2016-03-14 Moteur a combustion interne pourvu d'au moins un cylindre

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Publication Number Publication Date
EP3268597A1 EP3268597A1 (fr) 2018-01-17
EP3268597B1 true EP3268597B1 (fr) 2020-11-04

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EP (1) EP3268597B1 (fr)
JP (1) JP6688312B2 (fr)
CN (1) CN107567538B (fr)
AT (1) AT516161B1 (fr)
WO (1) WO2016145467A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP6969186B2 (ja) * 2017-07-19 2021-11-24 スズキ株式会社 エンジン及び自動二輪車

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AT326422B (de) * 1971-08-03 1975-12-10 List Hans Zylinderkopf für eine brennkraftmaschine
JPS5825860B2 (ja) * 1980-06-25 1983-05-30 三菱重工業株式会社 内燃機関のシリンダヘツド
JPS58180349U (ja) * 1982-05-28 1983-12-02 株式会社小松製作所 デイ−ゼルエンジン用シリンダヘツド構造
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WO2016145467A1 (fr) 2016-09-22
AT516161A4 (de) 2016-03-15
AT516161B1 (de) 2016-03-15
JP2018507984A (ja) 2018-03-22
JP6688312B2 (ja) 2020-04-28
CN107567538B (zh) 2020-07-07
CN107567538A (zh) 2018-01-09
EP3268597A1 (fr) 2018-01-17

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