EP2941545B1 - Abgasventilanordnung und verfahren zur steuerung des schliessens eines abgasventils - Google Patents

Abgasventilanordnung und verfahren zur steuerung des schliessens eines abgasventils Download PDF

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Publication number
EP2941545B1
EP2941545B1 EP13818759.6A EP13818759A EP2941545B1 EP 2941545 B1 EP2941545 B1 EP 2941545B1 EP 13818759 A EP13818759 A EP 13818759A EP 2941545 B1 EP2941545 B1 EP 2941545B1
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Prior art keywords
exhaust valve
fluid chamber
piston
outflow
closing
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EP13818759.6A
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English (en)
French (fr)
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EP2941545A1 (de
Inventor
Magnus Sundsten
Saku Niinikangas
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Wartsila Finland Oy
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Wartsila Finland Oy
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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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
    • 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
    • F01L9/14—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 the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing

Definitions

  • the present invention relates to an exhaust valve arrangement for a piston engine in accordance with the preamble of claim 1.
  • the invention also concerns a method for controlling closing of an exhaust valve of a piston engine, as defined in the preamble of the other independent claim.
  • VEC variable intake valve closing
  • VEC variable exhaust valve closing
  • VEC arrangements are often implemented by utilizing a chamber that is arranged between the exhaust valves and the cam operating the exhaust valves. The exhaust valves are opened in a conventional manner by the cam. During the opening movement of the exhaust valves, hydraulic fluid is introduced into the chamber.
  • the closing moment and closing speed of the exhaust valves depends on the outflow from the chamber. For instance, a closing delay can be provided by preventing the outflow by a valve.
  • a problem with this kind of solutions is that in case of malfunction of the system, closing of the exhaust valve can be prevented and the piston may hit the exhaust valve causing extensive damage.
  • An object of the present invention is to provide an improved exhaust valve arrangement for a piston engine, which arrangement allows a delay in the closing of the exhaust valve, but prevents the pistons of the engine from hitting the exhaust valves.
  • the characterizing features of the arrangement according to the invention are given in the characterizing part of claim 1.
  • Another object of the invention is to provide an improved method for controlling closing of an exhaust valve of a piston engine. Characterizing features of the method are given in the characterizing part of the other independent claim.
  • the arrangement according to the invention comprises at least one exhaust valve, a rotatable cam, force transmission means for transforming the rotating motion of the cam into linear motion and transmitting it to the exhaust valve at least in the opening direction of the exhaust valve, a fluid chamber, into which fluid chamber hydraulic fluid can be introduced during the opening movement of the exhaust valve, a piston that is arranged in the fluid chamber and connected to the force transmission means or to the exhaust valve, at least one outlet port for discharging the hydraulic fluid from the fluid chamber for allowing closing of the exhaust valve, and flow control means for controlling outflow from the fluid chamber and allowing slowing or delaying of the closing movement of the exhaust valve.
  • the outlet ports and the flow control means are configured to allow outflow from the fluid chamber at a rate that allows the closing curve of the exhaust valve to follow the cam curve at least until the exhaust valve has moved a certain predetermined distance in the closing direction.
  • hydraulic fluid is introduced into a fluid chamber during the cam-controlled opening movement of the exhaust valve, and outflow from the fluid chamber is controlled for affecting the movement of a piston that is arranged in the fluid chamber and connected to the exhaust valve or to force transmission means between a cam and the exhaust valve and for allowing slowing or delaying of the closing movement of the exhaust valve.
  • Outflow from the fluid chamber is allowed at a rate that allows the closing curve of the exhaust valve to follow the cam curve at least until the exhaust valve has moved a certain predetermined distance in the closing direction.
  • closing curve means the lift of the exhaust valve as a function of crank angle.
  • cam curve means the movement of a cam follower as a function of the crank angle.
  • the distance is determined so that the valve lift at the moment when the throttling starts is smaller than the distance between a closed exhaust valve and the piston of the engine in the respective cylinder at top dead center.
  • the closing curve of the exhaust valve corresponds thus first the cam curve, but after the throttling starts, the slope of the closing curve can be less steep than the slope of the cam curve.
  • the piston in the fluid chamber can be arranged to throttle the flow.
  • the end part of the piston can have smaller diameter than the rest of the piston.
  • the exhaust valve is fully open, also the outlet ports of the fluid chamber are fully open.
  • the piston has moved the predetermined distance, it covers one or more outlet ports, and outflow from the fluid chamber is allowed through a small gap that is formed between the piston and the wall of the fluid chamber.
  • Another option is to provide the fluid chamber with two or more outlet ports, which are at different heights, i.e. at different distances from the end of the fluid chamber.
  • the exhaust valve When the exhaust valve is fully open, also all the outlet ports are fully open.
  • the piston When the piston has moved the predetermined distance, it blocks at least one of the outlet ports and the outflow is thus restricted.
  • Some of the outlet ports or outlet ducts in connection with the outlet ports can be provided with throttles.
  • the throttles can be adjustable. It is also possible to provide some of the outlet ports or ducts with a valve, which allows adjustment of the outflow.
  • the exhaust valve arrangement according to the invention is especially suitable for large internal combustion engines, such as main or auxiliary engines of ships or engines that are used at power plants for producing electricity.
  • the invention is particularly useful in engines with two-stage turbocharging and in engines where water cooling of recirculated exhaust gases is used.
  • the arrangement can also be used in other types of engines.
  • valve opening mechanism for an exhaust valve 13.
  • each cylinder of the engine is provided with more than 1 exhaust valve 13, the valve opening mechanism can be used for controlling all the exhaust valves 13 of one cylinder.
  • the exhaust valve 13 is arranged in a cylinder head 18 for opening and closing fluid communication between a cylinder 16 of the engine and an exhaust duct 17.
  • a spring 15 is arranged around the stem of the exhaust valve 13 to keep the exhaust valve 13 closed when it is not actuated.
  • the valve opening mechanism is provided with a VEC-function for delaying the closing of the exhaust valve 13.
  • the valve opening mechanism comprises a cam 1, which is part of a camshaft.
  • the cam 1 is provided with a base circle 1 a and a lobe 1 b extending radially outwards from the base circle 1 a.
  • a cam follower wheel 2a of a cam follower unit 2 is constantly engaged with the cam 1.
  • the arrangement can be provided with a spring, which presses the cam follower wheel 2a against the cam 1.
  • the opening of the exhaust valves 13 works in a conventional manner.
  • the cam follower wheel 2a becomes engaged with the lobe 1 a of the cam 1, the cam follower unit 2 is pushed away from the rotation axis of the cam 1, i.e. upwards in figure 1 .
  • the cam follower unit 2 forms part of force transmission means 2, 3, 14, 19, which transform the rotating motion of the cam 1 into linear motion and further transmit the movement to the exhaust valves 13.
  • the force transmission means further comprise a first push rod 3, a second push rod 19 and a rocker arm 14.
  • the first push rod 3 is in mechanical contact with the cam follower unit 2 at least in the opening direction of the exhaust valves 13.
  • the second push rod 19 is connected to a rocker arm 14.
  • the rocker arm 14 transmits the movement of the second push rod 19 to the exhaust valves 13.
  • part of the force transmission path could be hydraulic.
  • the valve opening mechanism is provided with a fluid chamber 4, into which hydraulic fluid can be introduced during the opening movement of the exhaust valves 13.
  • the fluid chamber 4 is connected to an inlet duct 5 through an inlet port 5a. Hydraulic fluid can be introduced into the fluid chamber 4 through the inlet duct 5 and the inlet port 5a.
  • the arrangement could also be provided with two or more inlet ports 5a and/or ducts 5.
  • the inlet duct 5 is provided with a check valve 6, which allows flow into the fluid chamber 4 but not out of the chamber 4. Instead of the check valve 6, or in addition to it, the inlet duct 5 can be provided with a closing valve for selectively allowing or preventing flow into the fluid chamber 4.
  • the closing valve allows the VEC-function to be switched on and off. If the closing valve is closed, flow into the fluid chamber 4 is not allowed, and the VEC-function is switched off.
  • the valve opening mechanism works then in the same way as a conventional cam-controlled exhaust valve opening mechanism.
  • Figure 7 shows the valve lifts when the VEC is switched off. The hatched area shows the overlap of the exhaust and the intake valves.
  • a piston 7 is arranged in the fluid chamber 4.
  • the piston 7 delimits the fluid chamber 4 and the hydraulic fluid is introduced between the piston 7 and the camshaft end of the fluid chamber 4.
  • the piston 7 is connected to the first push rod 3 and the second push rod 19, i.e. the piston is between the first push rod 3 and the second push rod 19.
  • the first push rod 3 transmits the movement of the cam follower unit 2 to the piston 7 in the opening direction of the exhaust valves 13 and the second push rod 19 transmits the movement of the piston 7 to the rocker arm 14.
  • the fluid chamber 4 and the piston 7 could also be located in many other ways.
  • the fluid chamber 4 could be arranged inside the cylinder head 18 and the piston 7 could be connected to the stem of the exhaust valve 13, but this may be impractical.
  • the piston 7 can be connected to some other part of the force transmission means than the first push rod 3 and the second push rod 19. The piston 7 always moves together with the exhaust valves 13.
  • the closing speed of the exhaust valves can be slowed down.
  • the lift of the exhaust valve 13 is shown with a solid line and the cam curve is shown with a broken line.
  • the hatched area shows the overlap of the exhaust 13 and the intake valves.
  • FIG 2 is shown one arrangement for limiting outflow from the fluid chamber 4 of the valve opening mechanism of figure 1 .
  • the fluid chamber 4 is provided with one outlet port 8 and an outlet duct 9 that is in connection with the outlet port 8.
  • the outlet port 8 and the outlet duct 9 are dimensioned so that maximum flow rate through the outlet port 8 is adequate for allowing the piston 7 to follow the cam curve at the beginning of the closing movement of the exhaust valves 13.
  • the piston 7 starts to throttle the flow out of the fluid chamber 4. This happens when the camshaft end of the piston 7 is at the level of the outlet port 8, i.e. in phase 3 of figure 2 .
  • the diameter of the piston 7 at the camshaft end of the piston 7 is slightly smaller than the diameter of the rest of the piston 7.
  • the piston 7 does thus not block the outlet port 8 completely, but a small gap is formed between the piston 7 and the wall of the fluid chamber 4.
  • the hydraulic fluid can flow through this gap to the outlet port 8.
  • the flow is throttled so that the piston 7 is not able to follow the cam follower unit 2.
  • the piston 7 thus works as a flow control means and slows down the closing speed of the exhaust valves 13 so that a gap is formed between the first push rod 3 and the cam follower unit 2, as shown in phase 4 of figure 2 .
  • the slope of the closing curve of the exhaust valves 13 is less steep than the cam curve and the closing movement of the exhaust valves 13 continues when the cam follower wheel 2a has already returned to the base circle 1a of the cam 1.
  • the duration of the scavenging time is longer than in case the VEC is switched off.
  • the piston 7 is close to the camshaft end of the fluid chamber 4, the thicker part of the piston 7 partly blocks the outlet port 8, as shown in phase 5 of figure 2 .
  • the closing speed of the exhaust valves 13 is thus further decreased for allowing smooth closing.
  • the fluid chamber 4 is emptied and the first push rod 3 becomes engaged with the cam follower unit 2 again, as can be seen in phase 6 of figure 2 .
  • the piston 7 can have more than two different diameters to allow the closing speed of the exhaust valves 13 to change gradually, or the diameter of the piston 7 can decrease steplessly.
  • FIG 3 is shown another embodiment of the invention.
  • the operating principle of this embodiment is the same as in the embodiment of figure 1 .
  • hydraulic fluid is introduced into a fluid chamber 4 during the opening movement of the exhaust valves 13 and the piston 7 works as a flow control means.
  • the fluid chamber 4 is provided with a first outlet port 8a, a second outlet port 8b and a third outlet port 8c and with respective outlet ducts 9a, 9b, 9c.
  • the second outlet duct 9b is provided with a valve 10, which can be used for preventing flow in the second outlet duct 9b.
  • the valve 10 works as an additional flow control means. At the beginning of the closing movement of the exhaust valves 13, the hydraulic fluid can flow out of the fluid chamber through all the outlet ports 8a, 8b, 8c.
  • the outlet ports 8a, 8b, 8c and ducts 9a, 9b, 9c are dimensioned so that the exhaust valves 13 are able to follow the cam curve when the first and the third outlet ports 8a, 8c are free. This ensures that an adequate closing speed is achieved even if the valve 10 of the second outlet duct 9b is closed.
  • the piston 7 has moved a certain distance, it blocks the first outlet port 8a and the outflow from the fluid chamber 4 is restricted.
  • the piston 7 blocks also the second outlet port 8b, and the hydraulic fluid can flow out of the fluid chamber 4 only through the third outlet port 8c. This ensures that the exhaust valves 13 are closed smoothly.
  • the valve 10 in the second outlet duct 9b can be used for preventing flow through the second outlet port 8b even earlier.
  • the arrangement is provided with two outlet ports 8a, 8b and outlet ducts 9a, 9b.
  • the hydraulic fluid can flow out of the fluid chamber 4 through both the first outlet port 8a and duct 8b and the second outlet port 9a and duct 9b.
  • the outlet ports 8a, 8b and ducts 9a, 9b are dimensioned so that the exhaust valves 13 can follow the cam curve when both outlet ports 8a, 8b are open.
  • the second outlet duct 9b is provided with an adjustable throttle 11, which works as an additional flow control means. With the throttle 11, different closing curves can be achieved.
  • the throttle 11 can also be used to restrict the outflow more at the end of the closing movement of the exhaust valves 13 to ensure smooth closing.
  • the embodiment of figure 5 is similar to the embodiment of figure 4 .
  • the second outlet duct 9b is not provided with a throttle, but the second outlet duct 9b is connected to a second chamber 12, in which the cam follower unit 2 is arranged to move.
  • the cam follower wheel 2a is on the lobe 1 b of the cam 1
  • the cam follower unit 1 blocks the other end of the second outlet duct 9b.
  • the hydraulic fluid can freely flow out of the fluid chamber 4 through the first outlet port 8a.
  • the first outlet port 8a and the first outlet duct 9a are dimensioned so that the flow rate through the first outlet port 8a is adequate to allow the exhaust valves 13 to follow the cam curve.
  • FIG 6 shows an embodiment, where the arrangement is provided with two outlet ports 8a, 8b and outlet ducts 9a, 9b.
  • the second outlet duct 9b is provided with a quick-closing valve 10, which can be operated for example electrically or hydraulically.
  • the first outlet port 8a and the first outlet duct 9a are dimensioned so that the flow rate through the first outlet port 8a is adequate for allowing the exhaust valves 13 to follow the cam curve. This ensures that the fluid chamber 4 is emptied quickly enough even in case the valve 10 of the second outlet duct 9b does not work. At the beginning of the closing movement of the exhaust valves 13, outflow from the fluid chamber 4 is allowed both through the first outlet port 8a and the second outlet port 8b.
  • the piston 7 blocks the first outlet port 8a and outflow is allowed only though the second outlet port 8b.
  • the valve 11 in the second outlet duct 9b can be used for controlling the flow through the second outlet port 8b for achieving the desired exhaust valve closing curve.
  • the fluid chamber 4 can be provided with a third outlet duct, in which duct flow is prevented when the cam follower wheel 2a is on the base circle 1 a or the lobe 1 b of the cam 1.
  • the other end of the third outlet duct can be blocked by the cam follower unit 2.
  • the profile of the cam 1 is further provided with a portion that is below the base circle 1 a of the cam 1.
  • the throttling of the outflow takes place only after the exhaust valves have 13 been closed enough for preventing the piston of the cylinder 16 from hitting the exhaust valves 13.
  • the exhaust valve lift is thus smaller than the distance between a closed exhaust valve 13 and the piston at top dead center, as can be seen in figures 7 and 8 , which show also the movement of the piston around top dead center.
  • the predetermined distance after which the throttling of the outflow from the fluid chamber 4 can start, is determined such that contact between the exhaust valve 13 and the piston in the respective cylinder of the engine is prevented.
  • the lift of the exhaust valve 13 in the corresponding position is thus smaller than the distance between a closed exhaust valve 13 and the respective piston of the engine when the piston is at top dead center.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (12)

  1. Auslassventilanordnung für einen Kolbenmotor, wobei die Auslassventilanordnung Folgendes umfasst: mindestens ein Auslassventil (13), einen drehbaren Nocken (1), Kraftübertragungsmittel (2, 3, 14, 19) zum Umwandeln der Drehbewegung des Nockens (1) in eine lineare Bewegung und Übertragen auf das Auslassventil (13) mindestens in der Öffnungsrichtung des Auslassventils (13),
    eine Fluidkammer (4), wobei in diese Fluidkammer (4) während der Öffnungsbewegung des Auslassventils (13) Hydraulikfluid eingeführt werden kann,
    einen Kolben (7), der in der Fluidkammer (4) angeordnet und mit den Kraftübertragungsmitteln (2, 3, 14, 19) oder dem Auslassventil (13) verbunden ist, mindestens eine Auslassöffnung (8, 8a, 8b, 8c) zum Ablassen der Hydraulikfluids aus der Fluidkammer (4), um das Schließen des Auslassventils (13) zu ermöglichen,
    und Strömungssteuermittel (7, 10, 11) zum Steuern einer Ausströmung aus der Fluidkammer (4) und Ermöglichen einer Verlangsamung oder Verzögerung der Schließbewegung des Auslassventils (13), wobei die Auslassöffnungen (8, 8a, 8b, 8c) und die Strömungssteuermittel (7, 10, 11) konfiguriert sind, eine Ausströmung aus der Fluidkammer (4) bei einer Rate zu ermöglichen, bei der die Schließkurve des Auslassventils (13) der Nockenkurve mindestens bis zu dem Zeitpunkt folgen kann, bis sich das Auslassventil (13) um einen bestimmten vorbestimmten Abstand in der Schließrichtung bewegt hat, dadurch gekennzeichnet, dass die Ausströmung aus der Fluidkammer (4) ungedrosselt ist, bis sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat, und nachdem sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat, eine Drosselung der Ausströmung stattfindet, und dadurch, dass der Abstand derart bestimmt wird, dass der Ventilhub zu dem Zeitpunkt, wenn die Drosselung beginnt, geringer ist als der Abstand zwischen dem geschlossenen Auslassventil (13) und dem Kolben (7) des Kolbenmotors am Totpunktzentrum.
  2. Anordnung nach Anspruch 1, dadurch gekennzeichnet, dass der vorbestimmte Abstand derart bestimmt wird, dass in der entsprechenden Position des Auslassventils (13) ein Kontakt zwischen dem Auslassventil (13) und dem Kolben des Motors in dem jeweiligen Zylinder verhindert wird.
  3. Anordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Kolben (7) in der Fluidkammer (4) ausgelegt ist, eine Ausströmung aus der Fluidkammer (4) zu drosseln, nachdem sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat.
  4. Anordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Fluidkammer (4) mindestens zwei Auslassöffnungen (8, 8a, 8b, 8c) umfasst und der Kolben (7) ausgelegt ist, mindestens eine der Auslassöffnungen (8, 8a, 8b, 8c) zu blockieren, nachdem sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat.
  5. Anordnung nach Anspruch 4, dadurch gekennzeichnet, dass mindestens eine der Auslassöffnungen (8, 8a, 8b, 8c) oder eine Auslassleitung (9, 9a, 9b, 9c) in Verbindung mit der Auslassöffnung (8, 8a, 8b, 8c) mit einer Drossel (11) versehen ist.
  6. Anordnung nach Anspruch 5, dadurch gekennzeichnet, dass die Drossel (11) einstellbar ist.
  7. Anordnung nach Anspruch 4, dadurch gekennzeichnet, dass mindestens eine der Auslassöffnungen (8, 8a, 8b, 8c) oder eine Auslassleitung (9, 9a, 9b, 9c) in Verbindung mit der Auslassöffnung (8, 8a, 8b, 8c) mit einem Ventil (10) versehen ist.
  8. Verfahren zum Steuern des Schließens eines Auslassventils (13) eines Kolbenmotors, wobei in dem Verfahren während der nockengesteuerten Öffnungsbewegung des Auslassventils (13) Hydraulikfluid in eine Fluidkammer (4) eingeführt wird und eine Ausströmung aus der Fluidkammer (4) zum Beeinflussen der Bewegung eines Kolbens (7) gesteuert wird, der in der Fluidkammer (4) angeordnet und mit dem Auslassventil (13) oder Kraftübertragungsmitteln (2, 3, 14, 19) zwischen einem Nocken (1) und dem Auslassventil (13) zum Ermöglichen einer Verlangsamung oder Verzögerung der Schließbewegung des Auslassventils (13) verbunden ist, wobei in dem Verfahren eine Ausströmung aus der Fluidkammer (4) bei einer Rate ermöglicht wird, bei der die Schließkurve des Auslassventils (13) der Nockenkurve mindestens bis zu dem Zeitpunkt folgen kann, bis das Auslassventil (13) um einen bestimmten vorbestimmten Abstand in der Schließrichtung bewegt hat, dadurch gekennzeichnet, dass die Ausströmung ungedrosselt ist, bis sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat, und nachdem sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat, eine Drosselung der Ausströmung stattfindet, und dass der Abstand derart bestimmt wird, dass der Ventilhub zu dem Zeitpunkt, wenn die Drosselung beginnt, geringer ist als der Abstand zwischen dem geschlossenen Auslassventil (13) und dem Kolben (7) des Kolbenmotors am Totpunktzentrum.
  9. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass die Ausströmung durch Blockieren mindestens einer Auslassöffnung (8, 8a, 8b, 8c) der Fluidkammer (4) von dem Kolben (7) begrenzt wird.
  10. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass die Ausströmung durch Drosseln der Strömung von dem Kolben (7) begrenzt wird, nachdem sich das Auslassventil (13) um den vorbestimmten Abstand bewegt hat.
  11. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass die Ausströmung durch Drosseln der Strömung von mindestens einer Drossel (11) begrenzt wird, die in Verbindung mit einer Auslassöffnung (8, 8a, 8b, 8c) oder einer Auslassleitung (9, 9a, 9b, 9c) der Fluidkammer (4) angeordnet ist.
  12. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass die Ausströmung von mindestens einem Ventil (10) begrenzt wird, das in Verbindung mit einer Auslassöffnung (8, 8a, 8b, 8c) oder einer Auslassleitung (9, 9a, 9b, 9c) angeordnet ist.
EP13818759.6A 2013-01-03 2013-12-27 Abgasventilanordnung und verfahren zur steuerung des schliessens eines abgasventils Active EP2941545B1 (de)

Applications Claiming Priority (2)

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FI20135003A FI20135003L (fi) 2013-01-03 2013-01-03 Pakoventtiilijärjestely ja menetelmä pakoventtiilin sulkeutumisen kontrolloimiseksi
PCT/FI2013/051204 WO2014106681A1 (en) 2013-01-03 2013-12-27 Exhaust valve arrangement and method for controlling closing of an exhaust valve

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EP2941545A1 EP2941545A1 (de) 2015-11-11
EP2941545B1 true EP2941545B1 (de) 2016-11-23

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US9506382B2 (en) 2015-03-30 2016-11-29 Caterpillar Inc. Variable valve actuator
CN105781661B (zh) * 2016-03-14 2018-04-03 潍柴动力股份有限公司 发动机进气门回程可控装置及设有该装置的配气系统
JP2022133567A (ja) 2021-03-02 2022-09-14 エスケーマテリアルズジェイエヌシー株式会社 多環芳香族化合物

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KR102192961B1 (ko) 2020-12-18
CN104903552B (zh) 2017-11-03
CN104903552A (zh) 2015-09-09
FI20135003L (fi) 2014-07-04
EP2941545A1 (de) 2015-11-11
KR20150102118A (ko) 2015-09-04
WO2014106681A1 (en) 2014-07-10

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