EP3596317B1 - Steueranordnung für ein gaswechselventil in einer brennkraftmaschine und verfahren zum betrieb einer steueranordnung für ein gaswechselventil in einer brennkraftmaschine - Google Patents

Steueranordnung für ein gaswechselventil in einer brennkraftmaschine und verfahren zum betrieb einer steueranordnung für ein gaswechselventil in einer brennkraftmaschine Download PDF

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Publication number
EP3596317B1
EP3596317B1 EP17711180.4A EP17711180A EP3596317B1 EP 3596317 B1 EP3596317 B1 EP 3596317B1 EP 17711180 A EP17711180 A EP 17711180A EP 3596317 B1 EP3596317 B1 EP 3596317B1
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EP
European Patent Office
Prior art keywords
gas exchange
unit
cam follower
cam
valve
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EP17711180.4A
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English (en)
French (fr)
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EP3596317A1 (de
Inventor
Daniel HÄGGBLOM
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Wartsila Finland Oy
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Wartsila Finland Oy
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Publication of EP3596317A1 publication Critical patent/EP3596317A1/de
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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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • 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
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L2001/2427—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of an hydraulic adjusting device located between cam and push rod
    • 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
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L2001/256—Hydraulic tappets between cam and push rod

Definitions

  • the present invention relates to a control arrangement for a gas exchange valve adapted between a cam device and the gas exchange valve in an internal combustion piston engine according to the preamble of claim 1.
  • Invention relates also to method of operating a control arrangement of a gas exchange valve in an internal combustion piston engine.
  • the combustion of the fuel takes place in a confined space formed of a cylinder, a cylinder head and a piston of the engine, producing expanding gases that are used directly to provide mechanical power.
  • the gases in the confined space are changed to provide a fresh combustible charge in and remove exhaust gases from the cylinder.
  • the engine is provided with one or more gas exchange valves.
  • the operation of the gas exchange valve is synchronized with the position of the piston in the cylinder.
  • the gas exchange valve is connected to a valve lifting mechanism which moves the valve synchronous with the piston.
  • the valve lifting mechanism may be mechanical, hydraulic, electronic or a combination therefor.
  • Cam shafts are commonly used for providing the actuation of the lifting mechanism.
  • Cam shaft is provided with a cam surface with a cam profile which define and cause the operation of the valve lifting mechanism.
  • the cam profile may also be used for providing additional functionalities, examples of which can be found in the following documents.
  • WO2010012864 A1 discloses a control arrangement for gas exchange in a piston engine adapted between a cam device of a camshaft of the engine and an inlet valve mechanism arranged to open and close the inlet valve in association with a cylinder of the engine.
  • the control arrangement comprises a body part in which a piston device is movably arranged to be in force transmission connection with the camshaft and the valve mechanism.
  • the cam device includes a cam profile having a portion arranged under a base circle of the cam profile which portion of the cam profile is arranged to control gas exchange through the inlet valve for providing a delay in the closing of the inlet valve.
  • WO2012156573 A1 discloses at least one cam-operated valve lifting device for each cylinder of an engine, the valve lifting device being arranged to open a gas exchange valve.
  • the engine further comprises an arrangement for injecting additional oxygen containing gas into the cylinders of the engine, the arrangement comprising a pressure medium source for supplying the additional oxygen containing gas, an injection valve in connection with each cylinder, means for connecting the pressure medium source to the injection valves, and a control valve for each cylinder of the engine for controlling the operation of the injection valve.
  • Each control valve is arranged to be operated by a gas exchange cam of the respective cylinder.
  • WO2012156584 A1 discloses a multi-cylinder piston engine comprising at least one cam-operated valve lifting device for each cylinder of the engine, the valve lifting device being arranged to open a gas exchange valve, and a starting arrangement comprising a pressure medium source, at least one starting valve for introducing pressure medium into a cylinder of the engine, means for connecting the pressure medium source to the starting valves, and a control valve for each cylinder that is provided with a starting valve for controlling the operation of the starting valve.
  • Each control valve is arranged to be operated by a gas exchange cam of the respective cylinder.
  • the gas exchange is controlled by means of opening and closing timings of the valve, and the lift of the valve which should accurately controllable.
  • the operation of the engine is very sensitive to the operation of the gas exchange performance. Thus, any clearance or lash in the force transmission chain of the valve lifting mechanism should be minimised.
  • Document JPH08284620 A discloses a hydraulic type lash adjuster interposed in the valve system of an internal combustion engine. It is provided with a check valve allowing oil flow from a reservoir chamber to a pressure chamber, when a pressure difference over a fixed value is generated between the pressure chamber and the reservoir chamber. A non-return valve is opening when the pressure in the pressure chamber is over a fixed value.
  • Document EP0375742 B1 discloses a hydraulic engine valve lifter including a pair of pistons defining a pressure chamber there between and a separate lash adjusting piston which defines a lash adjustment chamber with one of the pistons in the pair.
  • One-way valve structures permit fluid to flow from the pressure chamber into the lash adjustment chamber thereby displacing the lash adjusting piston to, in turn, adjust valve lash.
  • US 4674451 A discloses a control arrangement for a gas exchange valve adapted between a cam device and the gas exchange valve in an internal combustion piston engine.
  • the arrangement comprises a cam profile in the cam device having a base circle and a portion arranged radially radially outside the base circle, a cam follower unit adapted to reciprocate under control of the cam profile, a first piston unit in force transmission connection via a hydraulic chamber with the cam follower unit, and configured to transmit valve lifting force from the cam device to the gas exchange valve for lifting the gas exchange valve, a hydraulic control space arranged between the first piston unit and the cam follower unit, a mechanical limiter configured to prevent movement of the first piston unit in a direction closing the valve at a predetermined location of the first piston unit, and a hydraulic fluid flow path opening into the hydraulic control space and connectable to a hydraulic fluid supply, adapted to fill the hydraulic control space with the hydraulic fluid.
  • An object of the invention is to provide a control arrangement by means of which the clearance in a force transmission system for actuating a gas exchange valve may be minimized.
  • a control arrangement for a gas exchange valve according to claim 1 is provided.
  • the cam device is advantageously a cam shaft which comprises a cylindrical rod or a shaft running the length of the cylinder bank(s) with a number of oblong lobes protruding from it, one for each gas exchange valve or a pair of valves, if so desired.
  • the cam lobes force the valves open by pressing on the valve, or on the force transmission system, as they rotate.
  • the hydraulic fluid flow path is provided with a non-return valve allowing flow in a direction towards the hydraulic control space and retaining the hydraulic fluid in the hydraulic control space.
  • the hydraulic fluid flow path is arranged to be closed or opened based on the location of the cam follower unit in respect to the body of the arrangement.
  • the respective openings of the hydraulic fluid flow path in the cam follower unit and in the body are coinciding when the cam follower unit rests on the portion of the cam profile radially inside the base circle of the cam profile.
  • Respectively the engageable, mating openings of the hydraulic fluid flow path in the cam follower unit and in the body are dislocated by the movement of the cam follower unit and the flow path is arranged to be closed.
  • the hydraulic fluid flow path between the hydraulic control space and the hydraulic fluid supply is configured to open and to close on the basis of the position of the cam follower unit.
  • the first piston unit is in force transmission connection with the cam follower via one or more mechanical links.
  • the system of one or more mechanical links between the first piston unit and the cam follower unit may be referred to simply as a force transmission system.
  • the hydraulic control space is formed by a cylinder bore arranged to the cam follower unit and a piston part extending from the first piston unit into the cylinder bore.
  • the hydraulic control space is formed by a cylinder bore arranged in the first piston unit and a piston part extending from the cam follower unit into the cylinder bore.
  • the first piston unit is configured to transmit valve lifting force in a hydraulic manner to the gas exchange valve for lifting the gas exchange valve.
  • the cam follower unit is arranged to a block of the engine and the first piston unit is arranged to a cylinder head of the engine.
  • the first piston unit is affected by a spring with a force that is stronger than hydraulic force obtainable from the hydraulic control space.
  • a method of operating a control arrangement according to claim 9 is provided.
  • the hydraulic fluid is retained in the hydraulic control space by arranging a non-return valve into a hydraulic fluid flow path between the hydraulic control space and the hydraulic fluid supply, allowing flow in a direction towards the hydraulic control space.
  • hydraulic fluid is retained in the hydraulic control space such that a hydraulic fluid flow path is closed by a non-return valve and allowing a gradual discharge of hydraulic fluid from the hydraulic control space via a gap between the piston part and the cylinder bore bordering the control space.
  • hydraulic fluid is retained in the hydraulic control space such that a hydraulic fluid flow path is closed by dislocation of mating openings of the hydraulic fluid flow path in the cam follower unit and in the body due to their relative movement.
  • FIG. 1 and 2 depicts schematically a gas exchange valve system 10 for an internal combustion piston engine 100.
  • the gas exchange valve system 10 comprises firstly a valve 12 arranged in connection with a gas channel 14 in a cylinder head 102 of the engine 100 (shown in the figure 3 ).
  • the gas exchange valve 12 opens or closes flow connection between the gas channel 14 and a combustion chamber 16 of the engine 100.
  • the valve 12 is moved, which is called as lifting, into its opening direction, by moving the valve against a biasing spring (not shown) by a valve control arrangement 20 in the engine 100.
  • the valve control arrangement 20 comprises a body 24 into which a generally cylindrical space 26 having a central axis 28 has been arranged. Even if not shown here, the different parts of the valve control arrangement 20 may be of different diameter.
  • the valve control arrangement 20 comprises or it functionally relates to a cam device 18, arranged rotatably in for example a cam shaft having a longitudinal axis 18'.
  • the cam device 18 is shown enlarged in the figure 2 .
  • the cam device 18 has a base circle 18.1 which is defined by a constant radius.
  • the cam profile is provided with a portion 18.4 arranged radially inside, i.e. below, the base circle 18.1 and a portion 18.3 radially outside, i.e. above, the base circle 18.1.
  • the cam profile means the outline of the cross section of the cam device 18.
  • the cam device 18 is configured to rotate in synchronous manner with a crank shaft of the engine 100 and thus also with the position of the piston(s) of the engine 100.
  • the valve control arrangement 20 further comprises a cam follower unit 22.
  • the cam follower unit comprises a body part 30 arranged into the space 26 of the body.
  • the body part 30 of the cam follower unit 22 has cylindrical guide surface 32 coaxial with the center axis 28 which guide surface 32 is arranged against the generally cylindrical space 26 of the body 24.
  • the cam follower unit 22 comprises also a cylindrical roller 23 which is arranged to rotate parallel to the longitudinal axis 18' of the cam device. The cam follower unit 22 reciprocates under control of the cam profile when the roller 23 follows the cam surface.
  • the valve control arrangement 20 comprises a first piston unit 34 which is in force transmission connection with the cam follower unit 22 and configured to transmit valve lifting force from the cam device 18 to the gas exchange valve 12.
  • the force transmission connection 52 between the gas exchange valve 12 and the first piston unit 34 is arranged to be substantially free from any play when the cam follower unit 22 is under guidance of the portions of the cam follower surface which are either on the base circle 18.1 or on the portion 18.3 radially outside, i.e. above, the base circle 18.1..
  • the force transmission connection is advantageously realized by hydraulic force transmission system using substantially incompressible fluid, such as lubrication oil of the engine 100.
  • the hydraulic force transmission system is coupled with the first piston unit 34 by mean of a stem 53.
  • Another option to provide corresponding effect is a direct, or solely mechanical integration of the gas exchange valve 12 with the first piston unit 34.
  • the first piston unit 34 and the cam follower unit 22 are connected by a hydraulic control space 36 arranged between the first piston unit 34 and the cam follower unit 22, such that the hydraulic control space 36 belongs to the force transmission system.
  • the hydraulic control space 36 is used for controlling an effective distance between the cam follower unit 22 and the first piston unit 34.
  • the arrangement is provided with a force device such as a spring 38 configured to push the first piston unit 34 towards the cam follower unit 22.
  • the first piston unit 34 is arranged here to the common cylindrical space 26 with the cam follower unit 22. As depicted by the cut portion in the figure 1 , the first piston unit 34 and the cam follower unit 22 may be arranged to separate bodies 24 but being mechanically connected via one or more mechanical links 40, which may be simply a push rod, as is shown in the figure 1 .
  • the limiter 42 is arranged to the body 24 of the first piston unit 34 longitudinally between the first piston unit 34 and the cam follower unit 22.
  • the limiter 42 is configured to prevent and stop movement of the first piston unit 34 in a direction closing the valve 12, at a predetermined location of the first piston unit 34 in the body 24.
  • the direction corresponds the direction towards the cam follower unit 22 in the configuration shown in the figure 1 , where the limiter 42 stops the movement of the first piston unit 34 at a predetermined distance from the cam device.
  • the limiter 42 is positioned such that the first piston unit 34 is against the limiter 42 when the cam follower unit 22 rests on the portion 18.4 of the cam profile radially inside the base circle 18.1. This position is shown in the Figure 5 .
  • a predetermined gap 35 which is formed between the first piston unit 34 and a stem 53.
  • the stem 53 belongs to the force transmission connection 52 between the gas exchange valve 12 and the first piston unit 34.
  • the stem 53 abuts on the body 24 of the valve arrangement by a shoulder or alike provided to the stem 53.
  • the gap 35 between the first piston unit 34 and a stem 53 is formed when the cam follower unit 22 shifts from the support of the base circle 18.1 to the support of the portion 18.4 arranged radially inside, i.e. below, the base circle 18.1 and the first piston unit 34 follows that movement.
  • the force device such as a spring 38 causes the first piston unit 34 to move against the limiter 42.
  • the cam follower unit 22 rests on the base circle 18.1 of the cam profile and at this position there is a gap 37 between the limiter 42 and the first piston unit 34.
  • the limiter 42 may be a notch or notches, a ring or a radial extension arranged inside the circular space provided for stopping the movement of the first piston unit 34.
  • the limiter may be realized also by a change of diameter of circular space for the first piston unit 34 in the body 24.
  • the first piston unit 34 and the cam follower unit 22 are connected in force transmission with each other via the hydraulic control space 36 arranged between the first piston unit 34 and the cam follower unit 22.
  • the hydraulic control space 36 is used for controlling the effective distance between the cam follower unit 22 and the first piston unit 34, including any possible links 40 adapted between the cam follower unit and the piston unit 34.
  • the hydraulic space 36 is filled with hydraulic fluid.
  • the arrangement is provided with the spring 38 which is configured to provide force which is greater than the force which the hydraulic control space is capable to provide. When the hydraulic fluid is lubrication oil of the engine the force which the hydraulic control space is capable to provide is proportional to the pressure of the lubrication oil.
  • the spring 38 is arranged behind the first piston unit, at opposite side to the hydraulic control space 36.
  • the hydraulic control space 36 is formed by a cylinder bore 46 in the cam follower unit 22 and a piston part 44 in the first piston unit 34 configured into the cylinder bore 46.
  • the piston part 44 is arranged to extend from the first piston unit 34 into the cylinder bore 46.
  • the link 40 is considered to be a part of the first piston unit 34.
  • the hydraulic control space 36 has a volume, and as is shown in the Figure 5 , when the cam follower rests on the portion of the cam profile below or radially inside the base circle of the cam profile, the first piston unit 34 is against the limiter 42.
  • the length of the link 40 is such that when the first piston unit is against the limiter 42 and the cam follower rests on portion of the cam profile radially inside the base circle 18.1 of the cam profile there is a play between the link 40 and the cam follower unit 22.
  • the valve control arrangement comprises a hydraulic fluid flow path 48 opening into the hydraulic control space 36 and also being connectable to a hydraulic fluid supply 50.
  • the hydraulic fluid flow path 48 is adapted to fill hydraulic control space with the hydraulic fluid obtainable from the hydraulic fluid supply 50.
  • the hydraulic fluid flow path is arranged to the cam follower unit 22 and it is connectable with the hydraulic fluid supply 50 via respective engageable openings 50', 50" in the cam follower unit 22 and the body 24 of the cam follower unit. This way the hydraulic fluid flow path 48 between the hydraulic control space 36 and the hydraulic fluid supply 50 is configured to open and to close on the basis of the position of the cam follower unit in respect to the body 24 thereof.
  • the fluid flow path is open only when the cam follower rests on portion of the cam profile radially inside the base circle 18.1 of the cam profile.
  • the hydraulic fluid flow path 48 is provided with a non-return valve 51 configured to allow fluid flow only in the direction towards the hydraulic control space 36. This provides the effect of supporting the maintenance of the pressure of the hydraulic fluid applied to the hydraulic control space 36 during the lift of the valve.
  • the piston part and the cylinder bore are configured so that only a minimal flow of hydraulic fluid takes place out from the control space 36 via a gap between the piston part 44 the cylinder bore 46 bordering the control space 36.
  • the gap is dimensioned so that mainly gas can escape through the gap. This provides an effect of bleeding any gas, such as the air, out of the hydraulic system
  • the cam device when the engine 100 is running the cam device is at rotation about its longitudinal axis 18' which causes back and forth movement of the cam follower unit 22 and the first piston unit 34, as well as the link or links 40 between them.
  • the hydraulic space when filled with pressurized hydraulic fluid, advantageously lubrication oil, participates in the force transmission system between the gas exchange valve and the cam follower unit and removes any lash otherwise present in the connections between the link of links 40, the cam follower unit and the first piston unit.
  • the gas exchange valve is opened i.e. lifted while the cam follower unit rests on the portion of the cam profile radially outside the base circle, and closed by the movement of the cam follower unit from the portion of the cam profile radially outside the base circle back to the base circle.
  • the force transmission system between the first piston unit and the cam follower unit is adjusted to zero clearance. This is performed by supplying hydraulic fluid into the hydraulic control space such it fills and pressurizes the hydraulic control space, which removes the clearance.
  • the flow path of the hydraulic fluid is closed by a non-return valve 51 which causes retaining the hydraulic fluid in the hydraulic control space while the lifting of the gas exchange valve is practised.
  • the hydraulic fluid is retained in the hydraulic control space by arranging a non-return valve 51 into a hydraulic fluid flow path 48 between the hydraulic control space 36 and the hydraulic fluid supply 50. Only a minimized discharge of hydraulic fluid from the hydraulic control space is allowed via a gap between the piston part and the cylinder bore bordering the control space 36.
  • the flow path supply of the hydraulic fluid is closed without a one-way valve. This is accomplished by misaligning the openings 50', 50" in the hydraulic fluid flow path 48, which causes retaining the hydraulic fluid in the hydraulic control space while the lifting of the gas exchange valve is practised. In this case the play between the cam follower unit 30 and the body must be adequately small to provide proper operation.
  • the size of the gaps is also substantially equal to the distance from the base circle 18.1 to the minimum radius 18.5 within the portion 18.4 of the cam profile radially inside the base circle 18.1.
  • said system is provided with an intentional play between the first piston unit 34 and the cam follower unit 22 which may be up to 2 mm, advantageously 1-2 mm.
  • the play is then compensated by the hydraulic control space 36.
  • the actual play depends on e.g. the size of the engine, but in large engines with push rods the tolerance chain can be very long from camshaft to cylinder head.
  • the distance between a counter surface 34' in the first piston unit 34 and the limiter 42 i.e. the gap 37, when the cam follower unit 22 rests on the base circle 18.1 is advantageously equal to the distance from the base circle 18.1 to the minimum radius 18.5 within the portion 18.4 of the cam profile radially inside the base circle 18.1. This way the tolerance chain is reduced to just one accurate measure which is utilized to adjust the system in accurate and efficient manner.
  • Figure 3 shows an embodiment of the invention in which the cam follower unit 22 (as well as a cam shaft) is arranged to a block 101 of the engine 100 and the first piston unit 34 is arranged to a cylinder head 102 of the engine 100.
  • the mechanical links 40 providing force transmission connection between is more complicated than just a single push rod, which increases the risk of additional play.
  • the present invention is particularly advantageous in the configuration shown in the figure 3 .
  • Mechanical links usually comprise pivoting lever arms to change the direction of the movement of the link.
  • the first piston unit 34 is in force transmission connection 52 with the gas exchange valve 12.
  • the force transmission connection 52 between the gas exchange valve 12 and the first piston unit 34 is arranged to be substantially free from any play.
  • the force transmission connection is advantageously realized by hydraulic force transmission system using substantially incompressible fluid, such as lubrication oil of the engine 100.
  • substantially incompressible fluid such as lubrication oil of the engine 100.
  • Another option is a direct integration of the valve 12 with the first piston unit 34.
  • the hydraulic control space 36 is operated in similar manner as in the embodiment of figure 1 for removing play in the links 40 between the first piston unit 34 and the cam follower unit 22.
  • FIG 4 there is shown an embodiment the hydraulic control space 36 which is formed by a cylinder bore 46 arranged at the end of the link 40 connected to the first piston unit, and a piston part 44 in the cam follower unit 22.
  • the piston part is extending from the cam follower unit 22 into the cylinder bore 46.
  • the operation is substantially similar to shown in the other figures.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Steueranordnung (20) für ein Gaswechselventil (12) eines Kolbenverbrennungsmotors, die Folgendes umfasst:
    - eine Nockenvorrichtung (18) mit einem Nockenprofil, wobei das Nockenprofil einen Grundkreis (18.1) und einen Abschnitt, der in Radialrichtung innerhalb (18.4) und in Radialrichtung außerhalb (18.3) des Grundkreises angeordnet ist, aufweist,
    - eine Nockenstößeleinheit (22), die angepasst ist, um sich unter der Steuerung des Nockenprofils hin- und herzubewegen,
    - eine erste Kolbeneinheit (34) in einer Kraftübertragungsverbindung mit der Nockenstößeleinheit (22) und dafür konfiguriert, zum Anheben des Gaswechselventils (12) eine Ventilhebekraft von der Nockenvorrichtung (18) zu dem Gaswechselventil (12) zu übertragen,
    - einen hydraulischen Steuerraum (36), der zwischen der ersten Kolbeneinheit (34) und der Nockenstößeleinheit (22) angeordnet ist, wobei die erste Kolbeneinheit (34) durch eine Feder (38) beeinflusst wird, die dafür konfiguriert ist, die erste Kolbeneinheit (34) mit einer Kraft, die stärker ist als eine hydraulische Kraft, die von dem hydraulischen Steuerraum (36) zu erlangen ist, hin zu der Nockenstößeleinheit (22) zu drängen,
    gekennzeichnet durch
    - einen mechanischen Begrenzer (42), der dafür konfiguriert ist, eine Bewegung der ersten Kolbeneinheit (34) in einer Richtung, die das Ventil bei einer vorbestimmten Position der ersten Kolbeneinheit (34) schließt, zu verhindern, wobei der Begrenzer (42) bei einer vorbestimmten Entfernung von der ersten Kolbeneinheit (34) angeordnet ist, wenn die Nockenstößeleinheit (22) auf dem Grundkreis des Nockenprofils ruht, wenn der hydraulische Steuerraum (36) unter Druck gesetzt ist, wobei die vorbestimmte Entfernung gleich einer maximalen radialen Abweichung des Abschnitts des Nockenprofils, in Radialrichtung innerhalb (18.4) des Grundkreises, von dem Grundkreis des Nockenprofils ist,
    - eine Hydraulikfluid-Strömungsbahn (48), die sich in den hydraulischen Steuerraum (36) öffnet und mit einer Hydraulikfluidzufuhr (50) verbunden werden kann, die angepasst ist, um den hydraulischen Steuerraum (36) mit dem Hydraulikfluid zu füllen, wobei die Hydraulikfluid-Strömungsbahn (48) dafür konfiguriert ist, sich auf der Grundlage der Position der Nockenstößeleinheit (22) zu öffnen und zu schließen.
  2. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass die Hydraulikfluid-Strömungsbahn (48) mit einem Rückschlagventil (51) versehen ist, das einen Strom in einer Richtung, hin zu dem hydraulischen Steuerraum (36), ermöglicht.
  3. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass die erste Kolbeneinheit (34) über eine oder mehrere mechanische Verknüpfungen (40) in einer Kraftübertragungsverbindung mit dem Nockenstößel steht.
  4. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass ein beabsichtigtes Spiel an dem Kraftübertragungssystem zwischen der ersten Kolbeneinheit (34) und der Nockenstößeleinheit (22) angeordnet ist, wenn der hydraulische Steuerraum nicht unter Druck gesetzt ist.
  5. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass der hydraulische Steuerraum (36) durch eine Zylinderbohrung (46), die an der Nockenstößeleinheit (22) angeordnet ist, und einen Kolbenteil (44), der sich von der ersten Kolbeneinheit (34) in die Zylinderbohrung (46) erstreckt, gebildet wird.
  6. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass der hydraulische Steuerraum (36) durch eine Zylinderbohrung (46) in der ersten Kolbeneinheit (34) und einen Kolbenteil (44), der sich von der Nockenstößeleinheit (22) in die Zylinderbohrung (46) erstreckt, gebildet wird.
  7. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass die erste Kolbeneinheit (34) dafür konfiguriert ist, zum Anheben des Gaswechselventils (12) auf eine hydraulische Weise eine Ventilhebekraft zu dem Gaswechselventil (12) zu übertragen.
  8. Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 1, dadurch gekennzeichnet, dass die Nockenstößeleinheit (22) an einem Block des Motors (100) angeordnet ist und die erste Kolbeneinheit (34) an einem Zylinderkopf des Motors (100) angeordnet ist.
  9. Verfahren zum Betreiben einer Steueranordnung (20) für ein Gaswechselventil (12) in einem Kolbenverbrennungsmotor (100), wobei das Verfahren die folgenden Schritte umfasst:
    a. Anordnen eines Nockenprofils in der Nockenvorrichtung (18), das einen Grundkreis (18.1) und einen Abschnitt, der in Radialrichtung innerhalb (18.4) angeordnet ist, und einen Abschnitt, der in Radialrichtung außerhalb (18.3) des Grundkreises (18.1) angeordnet ist, aufweist, und Drehen der Nockenvorrichtung (18) um ihre Längsachse (18'),
    b. Anordnen einer Nockenstößeleinheit (22), um sich unter der Steuerung des Nockenprofils hin- und herzubewegen, wobei die Drehbewegung der Nockenvorrichtung (18) in eine hin- und hergehende Bewegung der Nockenstößeleinheit (22) umgewandelt wird,
    c. Anordnen einer ersten Kolbeneinheit (34) in Kraftübertragungsverbindung mit der Nockenstößeleinheit (22), zum Übertragen einer Ventilhebekraft von der Nockenvorrichtung (18) zu dem Gaswechselventil (12),
    d. Anordnen eines hydraulischen Steuerraums (36) zwischen der ersten Kolbeneinheit (34) und der Nockenstößeleinheit (22), wobei die erste Kolbeneinheit (34) durch eine Feder (38) beeinflusst wird, die dafür konfiguriert ist, die erste Kolbeneinheit (34) mit einer Kraft, die stärker ist als eine hydraulische Kraft, die von dem hydraulischen Steuerraum (36) zu erlangen ist, hin zu der Nockenstößeleinheit (22) zu drängen,
    e. Anheben des Gaswechselventils (12), während die Nockenstößeleinheit (22) auf dem Abschnitt des Nockenprofils, in Radialrichtung außerhalb (18.3) des Grundkreises, ruht,
    f. Schließen des Gaswechselventils (12), während sich die Nockenstößeleinheit (22) von dem Abschnitt des Nockenprofils, in Radialrichtung außerhalb (18.3) des Grundkreises, zurück zu dem Grundkreis verlagert,
    gekennzeichnet durch Folgendes, während das Ventil geschlossen gehalten wird,
    g. Verhindern einer Bewegung der ersten Kolbeneinheit (34) in einer Richtung, die das Ventil bei einer vorbestimmten Position der ersten Kolbeneinheit (34) schließt, durch einen mechanischen Begrenzer (42), wobei der Begrenzer (42) bei einer vorbestimmten Entfernung von der ersten Kolbeneinheit (34) angeordnet ist, wenn die Nockenstößeleinheit (22) auf dem Grundkreis des Nockenprofils ruht, wobei die vorbestimmte Entfernung gleich einer maximalen radialen Abweichung des Abschnitts des Nockenprofils, in Radialrichtung innerhalb (18.4) des Grundkreises (18.1), von dem Grundkreis (18.1) des Nockenprofils ist,
    h. wenn der Nockenstößel auf dem Abschnitt des Nockenprofils, in Radialrichtung innerhalb (18.4) des Grundkreises des Nockenprofils, ruht, Zuführen von Hydraulikfluid in den hydraulischen Steuerraum (36), so dass es den hydraulischen Steuerraum (36) füllt und unter Druck setzt,
    i. Zurückhalten des Hydraulikfluids in dem hydraulischen Steuerraum (36), während das Anheben des Gaswechselventils (12) praktiziert wird.
  10. Verfahren zum Betreiben einer Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 9, dadurch gekennzeichnet, dass das Hydraulikfluid in dem hydraulischen Steuerraum (36) zurückgehalten wird durch Anordnen eines Rückschlagventils (51) in einer Hydraulikfluid-Strömungsbahn (48) zwischen dem hydraulischen Steuerraum (36) und der Hydraulikfluidzufuhr (50), was einen Strom in einer Richtung, hin zu dem hydraulischen Steuerraum (36), ermöglicht.
  11. Verfahren zum Betreiben einer Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 9, dadurch gekennzeichnet, dass das Hydraulikfluid in dem hydraulischen Steuerraum (36) derart zurückgehalten wird, dass eine Hydraulikfluid-Strömungsbahn (48) durch ein Rückschlagventil (51) geschlossen wird und eine allmähliche Abgabe von Hydraulikfluid aus dem hydraulischen Steuerraum (36) über einen Spalt zwischen dem Kolbenteil (44) und der Zylinderbohrung (46), die den Steuerraum (36) begrenzen, ermöglicht wird.
  12. Verfahren zum Betreiben einer Steueranordnung (20) für ein Gaswechselventil (12) nach Anspruch 9, dadurch gekennzeichnet, dass das Hydraulikfluid in dem hydraulischen Steuerraum (36) derart zurückgehalten wird, dass eine Hydraulikfluid-Strömungsbahn (48) durch eine Verlagerung von passenden Öffnungen der Hydraulikfluid-Strömungsbahn in der Nockenstößeleinheit und in dem Körper auf Grund von deren relativer Bewegung geschlossen wird.
EP17711180.4A 2017-03-17 2017-03-17 Steueranordnung für ein gaswechselventil in einer brennkraftmaschine und verfahren zum betrieb einer steueranordnung für ein gaswechselventil in einer brennkraftmaschine Active EP3596317B1 (de)

Applications Claiming Priority (1)

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PCT/EP2017/056340 WO2018166612A1 (en) 2017-03-17 2017-03-17 A control arrangement for a gas exchange valve in an internal combustion piston engine and method of operating a control arrangement for a gas exchange valve in an internal combustion engine

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EP3596317B1 true EP3596317B1 (de) 2023-05-03

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EP2941546B1 (de) * 2013-01-07 2016-12-21 Wärtsilä Finland Oy Steueranordnung und verfahren zur steuerung eines auslassventils

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EP2941546B1 (de) * 2013-01-07 2016-12-21 Wärtsilä Finland Oy Steueranordnung und verfahren zur steuerung eines auslassventils

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KR102084908B1 (ko) 2020-03-04
CN110418875A (zh) 2019-11-05
KR20190119642A (ko) 2019-10-22
CN110418875B (zh) 2021-03-30
WO2018166612A1 (en) 2018-09-20
EP3596317A1 (de) 2020-01-22

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