EP0620361B1 - Moteur à combustion interne avec arbre à came à tête et vilebréquin vertical - Google Patents

Moteur à combustion interne avec arbre à came à tête et vilebréquin vertical Download PDF

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Publication number
EP0620361B1
EP0620361B1 EP93119844A EP93119844A EP0620361B1 EP 0620361 B1 EP0620361 B1 EP 0620361B1 EP 93119844 A EP93119844 A EP 93119844A EP 93119844 A EP93119844 A EP 93119844A EP 0620361 B1 EP0620361 B1 EP 0620361B1
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EP
European Patent Office
Prior art keywords
oil
crankshaft
engine according
camshaft
transmission
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.)
Expired - Lifetime
Application number
EP93119844A
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German (de)
English (en)
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EP0620361A1 (fr
Inventor
Klaus Dr. Lück
Paul Kehl
Detlef Nonnenberg
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.)
ZF Sachs AG
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Fichtel and Sachs AG
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Publication of EP0620361A1 publication Critical patent/EP0620361A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/06—Dip or splash lubrication
    • 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
    • F02B75/007—Other engines having vertical crankshafts
    • 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
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/20—SOHC [Single overhead camshaft]
    • 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

Definitions

  • the invention relates to an internal combustion engine with a vertical crankshaft in a normal position of the engine, at least one overhead camshaft and a transmission between the crankshaft and the at least one camshaft with a plane of movement perpendicular to the crankshaft axis within a transmission space.
  • camshafts that are rotatably mounted in the cylinder head for direct or indirect actuation of the hanging intake and exhaust valves.
  • a transmission between the camshaft and crankshaft provides the required drive energy and at the same time ensures the necessary synchronization of the camshaft rotation with the crankshaft rotation.
  • the working shaft to be driven by the engine generally has a vertical orientation. An example of this is the sickle lawnmower. However, the vertical orientation is not always maintained, depending on the inclination of the surface, there is a corresponding inclination of the working wave.
  • crankshaft of the drive motor With regard to the simplest possible construction and high efficiency by avoiding frictional losses, a direct coupling of the crankshaft of the drive motor to the working shaft is of great advantage, at most with the interposition of a simple spur gear.
  • the crankshaft then also assumes a vertical orientation or, depending on the inclination of the subsurface, also an orientation that is more or less inclined to the vertical.
  • the at least one “overhead” camshaft extends laterally and axially parallel with respect to the camshaft axis.
  • an internal combustion engine of the type mentioned in which an oil pump in the area of the lower bearing point of the crankshaft for forced lubrication both of the particularly loaded crankshaft connecting rod bearing and the upper bearing point of the bearings located in the cylinder head, i.e. at the top Camshaft ensures.
  • the oil pump is connected to a through-channel of the crankshaft, which both has an outlet hole to the connecting rod bearing and also merges into cooling channels of a hollow flywheel flanged to the crankshaft in the region of the upper crankshaft end.
  • the cooling channels in turn open into a cooling channel running parallel to the cylinder axis within the hollow cylinder wall surrounding the piston. This cooling channel has both an exit point 38 (FIG.
  • the invention has for its object to provide an internal combustion engine of the type mentioned, which ensures reliable lubrication of the camshaft in the operating conditions occurring with a simple structure.
  • the transmission space is designed as an oil storage space in such a way that in the normal position and possibly in the inclined position of the engine, the lowest section of the transmission is immersed in the oil level.
  • the transmission thus serves as a delivery device for the lubricating oil, which always delivers the lubricating oil away from the current oil level and thus ensures a uniform distribution of the oil both in the area of the camshaft and in the area of the crankshaft. If, for example, the engine is currently inclined in such a way that the crankshaft space is lower than the camshaft space, the transmission dips into the oil level with its end on the crankshaft side, with the result that the transmission takes oil from there and conveys it into the camshaft area. Conversely, if the camshaft space is lower, oil is transferred from the transmission to the crankshaft space.
  • This oil distribution function of the transmission is also effective, for example, when the internal combustion engine is suddenly stopped or suddenly accelerated, so that the supply oil is currently jammed at the corresponding end of the oil storage space due to corresponding mass forces. A lack of oil at the other end of the oil reservoir is therefore ruled out by the transmission.
  • a transmission which is formed by an endless chain which runs via a gearwheel connected to the camshaft and a gearwheel connected to the crankshaft is particularly preferred on account of the simple structure and high oil output.
  • This chain can be a roller chain or a tooth chain.
  • the transmission can equally well be formed by an endless belt, preferably a toothed belt, which runs over a belt pulley connected to the camshaft and over a belt pulley connected with the crankshaft.
  • the toothed belt is characterized by its low weight and quiet running with good running precision. Both when using the chain and when using the belt, the inventive design of the transmission space as an oil reservoir promotes quiet running, since the oil bath for the chain or the belt contributes to significantly increased smoothness.
  • At least one oil channel be provided in the area of a bearing point of the crankshaft or camshaft for guiding deposited oil mist or spray oil to the respective bearing point.
  • the outlet of the oil pump is connected to a through-channel of the crankshaft with an outlet hole on the connecting rod bearing.
  • the through-channel can end at the connecting rod bearing, since the camshaft is lubricated independently of this due to the promotional effect of the transmission.
  • the oil pump is a rubber vane cell pump driven by the crankshaft.
  • part of the oil reservoir is an annular space surrounding the crankshaft.
  • the annular space can be produced inexpensively, since only a housing part to be attached to the crankcase needs to be modified accordingly.
  • the inlet of the oil pump via a feed line with the Annular space is connected, which opens into the annular space in the area of the annular space floor.
  • the supply line opens into the annular space on the side of the crankshaft axis diametrically opposite the camshaft. This position of the supply line ensures that the oil pump continues to be supplied with oil even in larger inclined positions of the engine.
  • the arrangement of the feed line on the side of the crankshaft axis facing away from the camshaft is intended for those cases in which a strong engine inclination in the sense of a higher-lying camshaft is permissible, but not a strong inclination in the opposite direction.
  • the camshaft is usually in front in relation to the direction of travel and, if the slope is steep, the lawnmower is allowed to go uphill, but not downhill.
  • the specified position of the oil pump intake opening ensures reliable bearing lubrication with compressed oil for driving uphill with a steep slope.
  • the annular space be provided with a cover arranged below the transmission.
  • the cover prevents the oil from flowing out of the annular space to such an extent that the intake opening of the oil pump reaches outside the oil level.
  • the cover be provided with at least one oil passage opening.
  • the at least one oil passage opening protrude upwards Circumferential band is provided.
  • the circumferential collar ensures that an oil pool with a depth corresponding to the circumferential collar height is formed on the cover.
  • the cover has a central opening through which the crankshaft passes.
  • At least one oil passage opening be arranged on the side of the crankshaft axis facing the at least one camshaft.
  • the cover is formed by a cover plate.
  • the internal combustion engine designated 10 thus has a crankshaft 12, the crankshaft axis 14 of which is oriented vertically in a normal position of the engine.
  • a camshaft 16 with an axis 18 parallel to the crankshaft axis 14 is rotatably mounted on a cylinder head 20 for the direct actuation of the hanging valves 22, in the example shown via bucket tappets 24, each of which engages around a valve spring 26.
  • crankshaft 12 is connected via a connecting rod 28 and a piston pin 30 to a cylinder 32 which is mounted in a cylinder crankcase 34 such that it can be moved back and forth.
  • the engine 10 shown is air-cooled, for which purpose corresponding cooling fins 34a and 20a are provided on the cylinder crankcase 34 and on the cylinder head 20 are.
  • the oil lubrication system to be described in more detail below can also be used with liquid-filled engines.
  • the cable pull starter 36 has the usual structure. It comprises a pull rope 36a, which is wound onto a rope sheave 36b, with the inner rope end fixed to this sheave. The outer end of the rope carries a handle, not shown. A rope tension spring 36c pretensions the rope pulley 36b in the sense of keeping the rope 36a wound up. Via a freewheel, not shown, the pulley 36b is coupled to a magnet wheel 38, which in turn is connected in a rotationally fixed manner (nut 39) to the upper end of the crankshaft 12.
  • the pole wheel 38 is formed with cooling fins 38a. Furthermore, the magnet wheel 38 carries at least one permanent magnet 38b as part of the magnetic ignition device 37. Each time the permanent magnet 38b passes an excitation unit 40 shown on the left of the magnet wheel 38 in FIG. 1, the required ignition voltage for the spark plug, not shown, is generated in the latter. Anchor plates 40a can be seen which increase the induction effect.
  • a conventional centrifugal governor 42 which acts on a throttle valve (not shown) for speed control.
  • a carrier part 42a for centrifugal weights 42b is provided with a circumferential toothing. This engages in a gearwheel 42c, which is attached in a rotationally fixed manner to a lower shaft journal 12b of the crankshaft 12 between a lower crank web 12a of the crankshaft 12 and a lower crankshaft bearing 44.
  • the centrifugal weights 42b serve to axially adjust an actuator 42d, which is in turn connected to the throttle valve by means not shown.
  • the pull starter 36 is covered on the outside by a cover cap 46.
  • a further cover cap 48 covers the magneto ignition device 37 together with the magnet wheel 38.
  • a cylinder head cover 50 covers the camshaft 16.
  • the lower crankshaft bearing 44 together with the centrifugal governor 42 are located in a separate housing part 52 which is attached to the cylinder crankcase 34.
  • the housing part 52 also houses an annular space 54 as part of the oil lubrication system still to be described and, in one version of the engine, an oil pump 56 in the form of a vane pump.
  • An upper crankshaft bearing 57 is inserted directly into the cylinder crankcase 34.
  • the camshaft 16 is driven synchronously with the crankshaft rotation via a transmission 60, which at the same time takes over the function of the lubricating oil distribution in order to ensure sufficient lubrication of the engine 10.
  • the transmission 60 is formed by an endless chain 62 (roller chain or toothed chain), which runs both via a gearwheel 64 attached to the lower end of the camshaft 16 and via a gearwheel 66 attached to the shaft journal 12b of the crankshaft 12 (see FIG. also top view according to FIG. 4).
  • the chain 62 can be tensioned by a tensioning device, not shown, depending on the type of engine. With a simple motor design, this may also be omitted.
  • the gearwheel 66 can form a common component with the gearwheel 42c mentioned above in the form of a gearwheel sleeve 67 pushed onto the shaft journal 12b and connected to it in a rotationally fixed manner.
  • an endless belt in particular a toothed belt, can also be used, which then runs over corresponding pulleys of the camshaft and the crankshaft.
  • the transmission space 70 receiving the transmission 60 within the engine 10 is simultaneously designed as an oil reservoir.
  • the chain 62 (or the belt in the case of a belt drive) is then immersed in the oil supply both in the normal position with an exactly vertical crankshaft axis 14 and in corresponding inclined positions, with the result that the chain conveys the oil away from the oil supply, i.e. in an area that currently has no standing oil.
  • Fig. 2 is intended to illustrate this.
  • One can see with a solid line an oil level 62a with an exact vertical ( perpendicular) orientation of the crankshaft axis 14.
  • the level 62a lies approximately such that the chain 60 and the gear wheels 64 and 66 are at least partially immersed in the lubricating oil. If the motor 10 is inclined, for example, by driving the lawn mower using the motor 10 up a slope, the oil level 62b is obtained, for example, with a slight inclination, provided that the usual design with the cylinder of the internal combustion engine pointing forward in the direction of travel is used.
  • both an upper and a lower pivot bearing 68a or 68b of the camshaft on the cylinder head have sufficient lubricating oil be supplied, as well as to the Cup tappets 26 adjoining cam surfaces 16a and 16b of the camshaft 16.
  • the cup tappets 26 themselves, if necessary, also receive sufficient lubricating oil within their respective guide bores in the cylinder head 20.
  • the motor is tilted in the opposite direction (driving downhill), e.g. an oil level 62c indicated with a dash-dot-dot line in FIG. 2.
  • the front gear 64 is immersed in the lubricating oil.
  • the chain 62 consequently conveys lubricating oil into the crankshaft space with its chain center 62a "returning to the gear 66 (arrow C in FIG. 4).
  • the consequence in turn is that in the region of the deflection of the chain 62 around the gear 66 oil splashes are thrown radially outwards 4.
  • the resulting oil splashes and oil mist ensure lubrication of both the crankshaft bearings 44 and 57 and generally a connecting rod bearing 72 between the connecting rod 28 and the crank pin 12c of the crankshaft 12.
  • the oil-producing effect of the transmission 60 which ensures the lubrication, from the current lubricating oil pool to regions remote from the pool is also present when the motor is inclined to the side, ie an inclination about a horizontal pivot axis 74 which is contained in one of the two axes 14 or 18 Level lies.
  • An oil level 62d is indicated in FIG. 4, which would result with a corresponding lateral inclination of the motor 10 (looking parallel to the axes 14 and 16). It can be seen that at least the front gear 64 is immersed in the oil, so that there is a conveying effect in the direction C, with oil splashes thrown in the direction of the arrows D and B when the chain rotates around the rear gear 66 and the front gear 64. Die Oil splashes or the oil mist ensures sufficient lubrication of all bearings.
  • a certain oil supply is necessary so that according to the invention the transmission 10 always runs partially through the standing lubricating oil even in the inclined positions mentioned.
  • the already mentioned annular space 54 is provided, which surrounds the shaft journal 12b.
  • a recess 76 can be provided in the region of the front gear 64 to form a corresponding oil pocket for storage oil.
  • the correspondingly large oil supply ensures, even with relatively extreme inclinations, that the transmission 60 is always partially immersed in the oil supply.
  • an oil level 62e is indicated by a dash-dot line, which is then assumed when the engine assumes the limit slope of 35 ° (travel uphill).
  • the rear gear 66 is still immersed in the oil reservoir.
  • the limit angle for downhill travel may be lower, because for safety reasons, downhill travel with a large incline is not permitted (risk of accident for the operator).
  • the constant, at least partial immersion of the transmission in the oil reservoir also has the advantage of reducing running noise.
  • the oil supply is dimensioned such that when the engine is inclined about the horizontal axis 74 in question by more than 90 °, the oil level 62d remains below the valves 22 and bucket tappets 24, so that hot and low-viscosity oil penetrates through the valve guides and the inlet valve in the combustion chamber or in the exhaust duct and the silencer is avoided from the outset.
  • Such a lateral motor inclination is necessary, for example, if the knife area is to be cleaned after use of the lawnmower or if maintenance or repair work on the cutting tool (sickle knife) is to be carried out.
  • the oil pump 56 already mentioned can be used for highly loaded engines. As FIG. 3 shows, the pump 56 receives oil from the annular space 54 via a feed line 56a. Since the motor should be particularly suitable for extreme rearward inclination (pivoting the motor about a horizontal axis in the clockwise direction of FIGS. 1 and 3) , the mouth 56b of the channel 56a lies on the side of the crankshaft axis 14 which is diametrically opposite the camshaft 16.
  • the oil pump 56 is connected to a through channel 80 of the crankshaft 12 via a radial branch line 80a.
  • the through channel 80 in turn ends at the connecting rod bearing 72 to form an outlet hole 80b.
  • the bearing that is most heavily loaded during operation, namely the connecting rod bearing 72, is consequently lubricated.
  • the remaining bearings are still lubricated with the aid of the delivery effect of the transmission 60.
  • the annular space 54 is provided with a cover 84 in the embodiment with an oil pump.
  • the cover 84 does not completely close off the annular space 54, but instead has oil passage openings which are adjusted to the oil delivery capacity of the oil pump 56. In many cases, it is sufficient to dimension a central opening 84a of the cover 84 through which the crankshaft 12 extends, so that there is a clear distance between the cover 84 and the crankshaft 12 (or sleeve 67 with the gearwheels 42c and 66).
  • 3 and 4 is one Oil passage opening 86 indicated. This lies on the side of the crankshaft axis 14 facing the camshaft 18. The reason for this is again that in the case of the strong inclined position to be taken into account in the first place with an inclined cylinder (limit angle 35 ° see FIG. 3) the mouth in any case 56b of the feed line 56a is below the oil level. This oil level adjusts itself to the level 62e according to FIGS. 2 and 3 at least initially. In the case of a smaller oil supply quantity than in FIG. 2, a level 62e ′ indicated in FIG. 3 is set after some time, which is defined by the lowest point of the central opening 84a. In any case, the opening 56b of the supply line 56a always remains in the lubricating oil bath.
  • the oil passage openings can each be provided with an upwardly projecting circumferential collar 88, which acts as a kind of " Overflow ".
  • the chain 62 always pumps oil from the oil pool formed on the cover into the areas of the engine which are more distant therefrom. No other moving parts are required for this type of lubrication, so that reliable operation with an inexpensive construction is ensured.
  • the small, light, single-cylinder four-stroke engine described above is suitable for driving implements, in particular a lawnmower.
  • Other operating modes with changing inclinations are also possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Harvester Elements (AREA)

Claims (19)

  1. Moteur à combustion interne (10) possédant un vilebrequin (12) orienté verticalement dans une position normale du moteur, au moins un arbre à cames (16) en tête et une transmission (60) prévue entre le vilebrequin (12) et l'arbre à cames (16) et ayant un plan de mouvement perpendiculaire à l'axe (14) du vilebrequin à l'intérieur d'un espace de transmission (70),
    caractérisé en ce que l'espace de transmission (70) est réalisé comme un espace de réserve d'huile, de manière qu'à la position normale ainsi que, éventuellement, à des positions inclinées du moteur, la partie de la transmission (60) située chaque fois au point le plus bas plonge dans le bain d'huile.
  2. Moteur à combustion interne selon la revendication 1, caractérisé en ce que la transmission (60) est formée par une chaîne (62) sans fin passant par un pignon (64) relié à l'arbre à cames (16) et par un pignon (66) relié au vilebrequin (12).
  3. Moteur à combustion interne selon la revendication 1, caractérisé en ce que la transmission est formée par une courroie sans fin, de préférence une courroie crantée, qui passe par une poulie à courroie reliée à l'arbre à came et par une poulie à courroie reliée au vilebrequin.
  4. Moteur à combustion interne selon une des revendications précédentes, caractérisé en ce qu'au moins une surface de rebondissement est prévue dans la zone de l'extrémité côté vilebrequin et/ou de l'extrémité côté arbre à cames de la transmission (60) pour l'huile éjectée par la transmission (60), afin de produire des projections d'huile ou du brouillard d'huile.
  5. Moteur à combustion interne selon la revendication 4, caractérisé en ce qu'au moins une gouttière de graissage est prévue dans la zone d'un palier du vilebrequin (12) et/ou de l'arbre à cames (16) pour diriger le brouillard d'huile déposé ou les projections d'huile vers le palier concerné.
  6. Moteur à combustion interne selon une des revendications précédentes, caractérisé par une pompe à huile (56) dont l'admission est raccordée à l'espace de réserve d'huile et dont la sortie est reliée à un palier de tête de bielle (76) sur le vilebrequin.
  7. Moteur à combustion interne selon la revendication 6, caractérisé en ce que la sortie de la pompe à huile (56) est raccordée à un canal traversant (80) du vilebrequin (12), canal qui présente un trou de sortie (80b) sur le palier de tête de bielle (72).
  8. Moteur à combustion interne selon la revendication 6 ou 7, caractérisé en ce que la pompe à huile (56) est une pompe cellulaire à ailettes en caoutchouc entraînée par le vilebrequin (12).
  9. Moteur à combustion interne selon une des revendications précédentes, caractérisé en ce qu'un espace annulaire (54) entourant le vilebrequin (12) fait partie de l'espace de réserve d'huile.
  10. Moteur à combustion interne selon une des revendications 6 à 9, caractérisé en ce que l'admission de la pompe à huile (56) est reliée à l'espace annulaire (54) par une canalisation d'arrivée (56a) qui débouche dans cet espace (54) dans la zone de son fond.
  11. Moteur à combustion interne selon la revendication 10, caractérisé en ce que la canalisation d'arrivée (56a) débouche dans l'espace annulaire (54) du côté de l'axe (14) du vilebrequin situé diamétralement à l'opposé de l'arbre à cames (16).
  12. Moteur à combustion interne selon une des revendications 9 à 11, caractérisé en ce que l'espace annulaire (54) est pourvu d'un recouvrement (84) placé sous la transmission (60).
  13. Moteur à combustion interne selon la revendication 12, caractérisé en ce que le recouvrement (84) est pourvu d'au moins un orifice de passage d'huile (86).
  14. Moteur à combustion interne selon la revendication 13, caractérisé en ce que l'orifice de passage d'huile (86) est pourvu d'un collet périphérique (88) faisant saillie vers le haut.
  15. Moteur à combustion interne selon la revendication 13 ou 14, caractérisé en ce que le recouvrement présente une ouverture centrale (84a) traversée par le vilebrequin (12).
  16. Moteur à combustion interne selon une des revendications 13 à 15, caractérisé par au moins un orifice de passage d'huile (86) du côté de l'axe (14) du vilebrequin dirigé vers l'arbre à cames (16).
  17. Moteur à combustion interne selon une des revendications 12 à 16, caractérisé en ce que le recouvrement (84) est formé par une tôle de recouvrement.
  18. Moteur à combustion interne selon une des revendications précédentes, caractérisé en ce qu'un évidement (76) situé sous l'arbre à cames (16) fait partie de l'espace de réserve d'huile.
  19. utilisation du moteur à combustion interne selon une des revendications précédentes dans une tondeuse à gazon.
EP93119844A 1993-04-16 1993-12-09 Moteur à combustion interne avec arbre à came à tête et vilebréquin vertical Expired - Lifetime EP0620361B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4312497 1993-04-16
DE4312497A DE4312497A1 (de) 1993-04-16 1993-04-16 Brennkraftmotor mit obenliegender Nockenwelle und vertikaler Kurbelwelle

Publications (2)

Publication Number Publication Date
EP0620361A1 EP0620361A1 (fr) 1994-10-19
EP0620361B1 true EP0620361B1 (fr) 1996-02-21

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EP93119844A Expired - Lifetime EP0620361B1 (fr) 1993-04-16 1993-12-09 Moteur à combustion interne avec arbre à came à tête et vilebréquin vertical

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US (1) US5447127A (fr)
EP (1) EP0620361B1 (fr)
DE (2) DE4312497A1 (fr)

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2852622B2 (ja) * 1994-12-22 1999-02-03 リョービ株式会社 縦軸エンジンおよびその潤滑装置
DE19503861C2 (de) * 1995-02-07 1999-07-22 Satzinger Gmbh & Co Verfahren zum dosierten Schmieren eines Kettentriebes, insbesondere eines Motorrad-Kettentriebes
US5755194A (en) * 1995-07-06 1998-05-26 Tecumseh Products Company Overhead cam engine with dry sump lubrication system
TW487770B (en) 1995-12-15 2002-05-21 Honda Motor Co Ltd Lubricating system in a 4-stroke engine
US6047678A (en) * 1996-03-08 2000-04-11 Ryobi North America, Inc. Multi-position operator-carried four-cycle engine
US6223713B1 (en) 1996-07-01 2001-05-01 Tecumseh Products Company Overhead cam engine with cast-in valve seats
JP3172103B2 (ja) * 1996-10-29 2001-06-04 本田技研工業株式会社 エンジンの動弁機構潤滑装置
JP3143783B2 (ja) * 1996-11-11 2001-03-07 本田技研工業株式会社 エンジンの潤滑及びブリーザ装置
JP3943660B2 (ja) * 1997-06-25 2007-07-11 三菱重工業株式会社 空冷４サイクル汎用エンジン
EP0995016B1 (fr) * 1997-07-07 2005-02-23 Mtd Products, Inc. Moteur a quatre temps fonctionnant en plusieurs positions
US6039020A (en) * 1998-03-05 2000-03-21 Ryobi Outdoor Products, Inc. Multiple-position, operator-carried, four-stroke engine
US5988129A (en) * 1998-09-21 1999-11-23 General Motors Corporation Engine lubrication system
JP2000161074A (ja) * 1998-11-27 2000-06-13 Kioritz Corp ４サイクル内燃機関
US6810849B1 (en) * 1999-01-25 2004-11-02 Briggs & Stratton Corporation Four-stroke internal combustion engine
EP1486652B1 (fr) * 1999-01-25 2006-10-18 BRIGGS & STRATTON CORPORATION Moteur à combustion interne à quatre temps
US6295959B1 (en) 1999-03-19 2001-10-02 Tecumseh Products Company External drive double shaft overhead cam engine
US6279522B1 (en) 1999-03-19 2001-08-28 Tecumseh Products Company Drive train for overhead cam engine
US6276324B1 (en) 1999-04-08 2001-08-21 Tecumseh Products Company Overhead ring cam engine with angled split housing
US6499453B1 (en) * 2000-10-30 2002-12-31 Tecumseh Products Company Mid cam engine
JP3894728B2 (ja) * 2000-12-28 2007-03-22 本田技研工業株式会社 エンジンにおける動弁用タイミング伝動装置
US20040083701A1 (en) * 2002-10-31 2004-05-06 Brower David R. Enclosed lawnmower engine with underdeck muffler
US7121248B2 (en) * 2003-05-26 2006-10-17 Honda Motor Co., Ltd. Vertical engine
CN1746467B (zh) * 2004-09-11 2010-05-05 Avl里斯脱有限公司 用于草坪修整机的四冲程内燃机
DE102004050056A1 (de) * 2004-10-14 2006-04-27 Bayerische Motoren Werke Ag Maschinengehäuse für eine Brennkraftmaschine
DE602005018556D1 (de) * 2005-09-27 2010-02-04 Dayco Europe Srl Mit einem schuh versehener riementrieb zur verwendung in öl
DK200900525A (en) * 2009-04-23 2010-10-24 Timan Dev As Mower with actively lubricated engine
DK200900522A (en) * 2009-04-23 2010-10-24 Timan Dev As Vehicle such as a mower with suspended tracks
DE102010005827A1 (de) * 2010-01-27 2011-07-28 GM Global Technology Operations LLC, ( n. d. Ges. d. Staates Delaware ), Mich. Ölversorgungseinrichtung
DE102013219940A1 (de) * 2013-10-01 2015-04-02 Bayerische Motoren Werke Aktiengesellschaft Hubkolben-Brennkraftmaschine mit einer Kurbelwelle
DE102017120109B4 (de) 2017-08-31 2019-05-23 ikra GmbH Schmiervorrichtung und Verbrennungsmotor mit einer solchen Schmiervorrichtung
WO2019187113A1 (fr) * 2018-03-30 2019-10-03 本田技研工業株式会社 Moteur
US11085394B2 (en) 2018-03-30 2021-08-10 Honda Motor Co., Ltd. Engine

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1057822B (de) * 1955-12-08 1959-05-21 Maschf Augsburg Nuernberg Ag OElumlaufsystem bei Verbrennungsmotoren, insbesondere fuer gelaendegaengige Fahrzeuge
US4611559A (en) * 1983-09-13 1986-09-16 Sanshin Kogyo Kabushiki Kaisha Outboard motor provided with a four-stroke engine
JPS60209616A (ja) * 1984-04-02 1985-10-22 Fuji Heavy Ind Ltd Ｏｈｃエンジンの潤滑装置
US4756280A (en) * 1984-12-21 1988-07-12 Kawasaki Jukogyo Kabushiki Kaisha Cooling system for vertical shaft V-type engine
US5000126A (en) * 1986-10-01 1991-03-19 Yamaha Kogyo Hatsudoki Kabushiki Kaisha Vertical engine for walk-behind lawn mower
JPS63147906A (ja) * 1986-12-09 1988-06-20 Kawasaki Heavy Ind Ltd エンジンのカム軸の構造
JPS63209509A (ja) * 1987-02-27 1988-08-31 ヤマハ発動機株式会社 芝刈機の内燃機関冷却装置
US4727834A (en) * 1987-06-09 1988-03-01 Yamaha Hatsudoki Kabushiki Kaisha Vertical engine for walk behind lawn mower
JPH0178209U (fr) * 1987-11-13 1989-05-25
JPH0729209Y2 (ja) * 1987-12-21 1995-07-05 富士重工業株式会社 バーチカルシャフトエンジンのブリーザ装置
JPH0290306U (fr) * 1988-12-27 1990-07-18
US5031591A (en) * 1989-01-30 1991-07-16 Honda Giken Kogyo Kabushiki Kaisha OHC vertical crankshaft engine
US4984539A (en) * 1989-05-15 1991-01-15 Honda Giken Kogyo Kabushiki Kaisha Liquid cooled internal combustion engine
US5090375A (en) * 1990-11-26 1992-02-25 Tecumseh Products Company Valve gear oiling system for overhead camshaft engine
JP2502550Y2 (ja) * 1991-12-27 1996-06-26 株式会社椿本チエイン タイミングチェ―ンの潤滑構造

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DE59301686D1 (de) 1996-03-28
EP0620361A1 (fr) 1994-10-19
DE4312497A1 (de) 1994-10-20

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