EP3440323B1 - Dispositif de commande variable de soupape d'admission et d'échappement et moteur comprenant un tel dispositif - Google Patents

Dispositif de commande variable de soupape d'admission et d'échappement et moteur comprenant un tel dispositif Download PDF

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Publication number
EP3440323B1
EP3440323B1 EP17713160.4A EP17713160A EP3440323B1 EP 3440323 B1 EP3440323 B1 EP 3440323B1 EP 17713160 A EP17713160 A EP 17713160A EP 3440323 B1 EP3440323 B1 EP 3440323B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
operative connection
hydraulic path
inlet
Prior art date
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Application number
EP17713160.4A
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German (de)
English (en)
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EP3440323A1 (fr
Inventor
Wolfgang Fimml
Jonathan Lipp
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.)
Rolls Royce Solutions GmbH
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MTU Friedrichshafen GmbH
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Publication of EP3440323A1 publication Critical patent/EP3440323A1/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
    • 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
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a valve drive for the variable control of an inlet valve and an outlet valve of a combustion chamber of an internal combustion engine as well as an internal combustion engine with such a valve drive.
  • a first operative connection is established between a valve actuation device and the inlet valve, a second operative connection being established between the valve actuation device and the outlet valve.
  • At least the first operative connection is assigned an interruption element which is set up to temporarily interrupt the first operative connection.
  • the second operative connection can also be assigned an interruption element which is set up to temporarily interrupt the second operative connection.
  • each of the operative connections is assigned an interruption element, hence the first operative connection a first interruption element and the second operative connection a second interruption element different from the first interruption element .
  • this configuration is expensive and difficult to integrate into an existing internal combustion engine, primarily for reasons of space. In particular, the space requirement is very large due to the two separate interruption elements.
  • the invention is based on the object of creating a valve drive and an internal combustion engine with such a valve drive, the disadvantages mentioned not occurring.
  • the object is achieved in particular by creating a valve drive for the variable control of an inlet valve and an outlet valve of a combustion chamber of an internal combustion engine, which valve drive has a first operative connection between a valve actuation device and the inlet valve, wherein it also has a second operative connection between the valve actuation device and the outlet valve.
  • the first and the second operative connection are assigned an interruption element which is set up for the temporary interruption of the operative connections, the first operative connection and the second operative connection being connected to the same interruption element in such a way that the first and the second operative connection through the same interruption element temporarily - in particular alternately - can be interrupted.
  • the opening edges for the inlet valve on the one hand and the outlet valve on the other hand are offset in time to one another, in particular the actuation cycles for the inlet valve on the one hand and the outlet valve on the other hand being out of phase with one another, makes it possible to have variable control for both the inlet valve and the outlet valve to effect with only one and in particular exactly one interruption element, which can temporarily interrupt the first operative connection in particular at a first point in time within a work cycle of the combustion chamber, with the second operative connection at a second point in time within the work cycle that is different from the first point in time can temporarily interrupt.
  • a valve drive is understood here in particular as a mechanism or a facial expression which is set up to actuate gas exchange valves that are assigned to a combustion chamber of an internal combustion engine, in particular an inlet valve and an outlet valve.
  • the valve train can have mechanical, hydraulic, electrical, electronic and / or other types of elements that serve to actuate the gas exchange valves.
  • An operative connection between a valve actuation device and a valve is in particular a connection or Understood coupling between the valve actuation device and the corresponding valve, which enables the valve to be actuated by the valve actuation device, and therefore in particular to be opened and / or closed.
  • the operative connection can in principle be of a mechanical, hydraulic, pneumatic, electrical, electronic or other type.
  • a valve actuation device is understood to mean, in particular, a device which is set up to actuate a valve, in particular to open or close it, in particular to specify control times for an opening time, for a closing time and preferably also a valve lift for the valve.
  • the valve actuation device can in particular have at least one camshaft with at least one cam, a plurality of camshafts and / or a plurality of cams, or other types of means for valve actuation.
  • the valve actuation device acts in particular on a first operative end of an operative connection, which acts with a second operative end on the valve, here on the inlet valve or the outlet valve. It is possible for the same valve actuation device to be assigned to the first operative connection and the second operative connection. However, it is also possible that a first valve actuation device is assigned to the first operative connection, a second valve actuation device different from the first valve actuation device being assigned to the second operative connection.
  • first operative connection to exist between a first actuation element and the inlet valve
  • second operative connection to exist between a second actuation element and the outlet valve.
  • first operative connection to exist between an actuation element and the inlet valve
  • second operative connection to exist between the same actuation element and the outlet valve.
  • the actuating elements can in particular be first and second cams of the same camshaft or different camshafts, but also first and second Act elevations on the same cam of a camshaft.
  • An interruption element is understood to mean, in particular, an element which is set up to temporarily interrupt an operative connection between a valve actuation device and a valve, in particular in which the operative connection is canceled, for example by mechanical disconnection, releasing hydraulic or pneumatic pressure, disconnecting an electrical connection , electronic inactivation of the active compound, or the like.
  • the first operative connection and the second operative connection are designed as hydraulic operative connections, the interruption element being designed as a switching valve.
  • the interruption element is designed as a 2/2-way valve.
  • the first operative connection has a first hydraulic path to a first slave cylinder, the second operative connection having a second hydraulic path to a second slave cylinder, the interruption element being connected to the first hydraulic path and to the second hydraulic path.
  • hydraulic medium can be diverted from both the first hydraulic path and from the second hydraulic path - at different times - via the interruption element.
  • the interruption element can be brought into fluid connection in particular with the first hydraulic path and also with the second hydraulic path - at different times - in particular via interruption check valves which are set up to open the fluid connections twice and to block them twice.
  • a slave cylinder is understood to mean, in particular, a hydraulic cylinder which is set up to receive hydraulic fluid from a master cylinder, the slave cylinder being connected to a valve, here with the inlet valve or the outlet valve, in such a way that the valve is actuated, in particular opened when the slave cylinder receives hydraulic fluid from the master cylinder.
  • the first hydraulic path is preferably formed between a first master cylinder and the first slave cylinder.
  • the second hydraulic path is preferably formed between a second master cylinder and the second slave cylinder. In this case, different master cylinders are assigned to the inlet valve and the outlet valve.
  • the interruption element is connected to both the first hydraulic path and the second hydraulic path via the same fluid connection.
  • a 2/2-way valve has two fluid connections as an interruption element, whereby it is preferably connected to a first fluid connection with the first hydraulic path and the second hydraulic path, whereby it can be in fluid connection with the second fluid connection with a hydraulic fluid reservoir, in which from the Hydraulic fluid controlled by hydraulic paths can be temporarily stored.
  • the interruption means preferably has only one fluid connection for both hydraulic paths and not, for example, a separate fluid connection for each hydraulic path, which, however, is basically also conceivable.
  • the interruption element is connected to the first hydraulic path via a first interruption check valve, the interruption element being connected to the second hydraulic path via a second interruption check valve.
  • the interruption check valves are preferably arranged fluidically parallel to one another. In particular, downstream of the common fluid connection of the interruption element for the two hydraulic paths there is a branch to the first interruption check valve on the one hand and the second interruption check valve on the other.
  • the interruption check valves are preferably in the direction away from the interruption element Direction biased in a closed position.
  • interruption check valves are therefore provided in particular to separate the hydraulic paths from one another so that, despite the common interruption element, a clear valve opening behavior is guaranteed for both the inlet valve and the outlet valve.
  • the interruption element is in fluid connection with a hydraulic medium reservoir.
  • the interruption element with its second fluid connection which is different from the first fluid connection connected to the hydraulic paths, is in fluid connection with the hydraulic medium reservoir.
  • the interruption element is set up in particular to alternately bring the first hydraulic path and the second hydraulic path and at times none of the hydraulic paths into fluid connection with the hydraulic medium reservoir.
  • the interruption element is particularly designed to fluidically connect its first fluid connection to its second fluid connection in a first switching position and to block the fluid connection between its first fluid connection and its second fluid connection in a second switching position.
  • first hydraulic path or the second hydraulic path is then connected to the hydraulic fluid reservoir in the first switching position is preferably not decided by the switching position of the interruption element, but rather this depends on the instantaneous pressure conditions in the hydraulic paths. If hydraulic pressure is built up in the first hydraulic path to actuate the inlet valve during a working cycle of the combustion chamber during a first period of time, the interruption element can be shifted into its first switching position in order to divert hydraulic fluid from the first hydraulic path and thus effect variable actuation of the inlet valve. In this case, the second interruption check valve prevents hydraulic medium from flowing into the second hydraulic path and from there causing an undesired actuation of the outlet valve.
  • the interruption element can be switched into its first switching position in order to remove hydraulic medium from the second hydraulic path to be controlled and thus to effect a variable actuation of the exhaust valve.
  • the first interruption check valve prevents hydraulic medium from flowing into the first hydraulic path and from causing undesired actuation of the inlet valve there.
  • the interruption element is preferably arranged in its second switching position.
  • the object is also achieved by creating an internal combustion engine which has a valve drive according to one of the exemplary embodiments described above.
  • the advantages that have already been explained in connection with the valve drive are realized in particular.
  • the internal combustion engine preferably has a plurality of combustion chambers, each combustion chamber being assigned at least one inlet valve and at least one outlet valve. It is possible for more than one inlet valve and / or more than one outlet valve to be assigned to each combustion chamber, it being possible in particular for two inlet valves and two outlet valves to be provided per combustion chamber.
  • the inlet valves and the outlet valves of each combustion chamber are assigned to one another in pairs, an interruption element being assigned to each valve pair comprising an inlet valve and an outlet valve of the same combustion chamber. Each pair of valves is preferably assigned exactly one and only one interruption element.
  • a combustion chamber has more than one inlet valve and / or more than one outlet valve
  • several inlet and / or outlet valves of the same combustion chamber can also be assigned to one another and be operatively connected to exactly one and only one interruption element.
  • a combustion chamber it is possible for a combustion chamber to have exactly two inlet valves and exactly two outlet valves, the two inlet valves and the two outlet valves being assigned to one another, so that exactly one interruption element is provided for all four valves.
  • the internal combustion engine has a control device, the control device having a control means for each interruption element assigned to a valve pair.
  • the control device preferably has precisely one control means for each interruption element.
  • Such a control means is preferably designed, in particular, as an electronic amplification means, in particular as an output stage.
  • the internal combustion engine has a control device - in particular the control device explained above - which is set up to control the at least one interruption element at least twice per work cycle of the combustion chamber assigned to the interruption element.
  • the control device is preferably set up to control each interruption element assigned to a combustion chamber at least twice per work cycle of the respective combustion chamber.
  • the internal combustion engine is preferably designed as a reciprocating piston engine. It is possible that the internal combustion engine is set up to drive a passenger car, a truck or a commercial vehicle. In a preferred exemplary embodiment, the internal combustion engine is used to drive particularly heavy land or water vehicles, for example mining vehicles, trains, the internal combustion engine being used in a locomotive or a railcar, or ships. It is also possible to use the internal combustion engine to drive a vehicle used for defense, for example a tank. An embodiment of the internal combustion engine is preferably also used in a stationary manner, for example for stationary energy supply in emergency power operation, continuous load operation or peak load operation, the internal combustion engine in this case preferably driving a generator.
  • the internal combustion engine is preferably designed as a diesel engine, as a gasoline engine, as a gas engine for operation with natural gas, biogas, special gas or another suitable gas.
  • the internal combustion engine as Gas engine is designed, it is suitable for use in a combined heat and power plant for stationary energy generation.
  • Fig. 1 shows a schematic representation of an example of a valve drive 1 for variable control of an inlet valve 3.
  • the inlet valve 3 is assigned to a combustion chamber 7, which is only indicated schematically here, of an internal combustion engine 9, which is also only indicated schematically.
  • the valve drive 1 has a first operative connection 11 between a valve actuation device 13, here specifically between a first actuation element 15, which is designed as a cam of a camshaft, and the inlet valve 3.
  • This first operative connection 11 is designed as a hydraulic operative connection and comprises a first hydraulic path 17.
  • the first hydraulic path 17 has a first master cylinder 19, which interacts with the first actuating element 15, and a first slave cylinder 21, the first master cylinder 19 during a rotary movement of the first actuating element 15 is caused to move, by means of which hydraulic medium is forced out of the first master cylinder 19 via the first hydraulic path 17 into the first slave cylinder 21, the first slave cylinder 21 being operatively connected to the inlet valve 3 in such a way that it is fed by the first slave cylinder 21 is urged into an open position against the biasing force of a biasing element 23, in particular a spring.
  • a first check valve 25 and a first bypass 27 bypassing the first check valve 25 in which a first throttle element 29 is arranged are arranged between the first master cylinder 19 and the first slave cylinder 21.
  • the first check valve 25 can open so that hydraulic medium can flow to the slave cylinder 21 via the first check valve 25. If the first actuation element 15 continues to rotate, a volume in the first master cylinder 19 is increased again so that hydraulic medium can flow back into it. At the same time, the hydraulic medium in the first slave cylinder 21 is pressurized by the prestressing element 23. In this operating state, the first check valve 25 is pushed into its blocking position. The hydraulic medium then flows from the first slave cylinder 21 via the first bypass 27 and the first throttle element 29 back into the first master cylinder 19, with the inlet valve 3 being shifted into its closed position at the same time.
  • the closing behavior of the inlet valve 3 is determined in particular by the first biasing element 23 on the one hand and the first throttle element 29 on the other hand, in particular by their coordination with one another.
  • the valve drive 1 has a first interruption element 31 assigned to the first operative connection 11, which is set up to interrupt the first operative connection 11 twice.
  • the first interruption element 31 is preferably designed as a switching valve, here in particular as a 2/2-way valve.
  • the first interruption element 31 is connected to a first fluid connection 33 - on the side of the first master cylinder 19 - with the first hydraulic path 17. With a second fluid connection 35, the first interruption element 31 is in fluid connection with a hydraulic medium reservoir 37.
  • the first interruption element 31 is designed to establish a fluid connection between the first fluid connection 33 and the second fluid connection 35 and thus at the same time between the first hydraulic path 17 and the hydraulic fluid reservoir 37 in a first switching state, and to establish the fluid connection between the fluid connection in a second switching state shown here to interrupt the first fluid connection 33 and the second fluid connection 35.
  • a variable control of the inlet valve 3 is now brought about by the first interruption element 31 according to the lost motion principle, for example by shifting it to its first switching state at a predetermined point in time during a stroke movement of the first valve 3, whereby the fluid connection between the first hydraulic path 17 and the hydraulic fluid reservoir 37 is released.
  • the hydraulic fluid displaced from the first master cylinder 19 is then - at least partially - diverted into the hydraulic fluid reservoir 37 via the first interruption element 31, whereby the pressure in the first hydraulic path 17 on the side of the first master cylinder 19 drops so that the first check valve 25 blocks.
  • valve lift of the inlet valve 3 is interrupted and this closes, with hydraulic medium from the first slave cylinder 21 also being displaced into the hydraulic medium reservoir 37 by the prestressing force of the prestressing element 23 via the first bypass 27 and the first throttle element 29 and further via the first interruption element 31 .
  • a delayed valve lift of the inlet valve 3 can also be brought about by shifting the first interruption element 31 to its first switching state at the beginning of the lifting movement of the first master cylinder 19 and moving it to its second switching state only later during the lifting movement of the first master cylinder 19. It is therefore possible to represent a fully variable valve drive for the inlet valve 3 by means of the first interruption element 31.
  • the first interruption element 31 remains in its second switching state during a working cycle of the internal combustion engine 9, a normal valve lift of the inlet valve 3 is effected, the lift curve of which is essentially determined by the design, in particular the shape, of the first actuating element 15.
  • the first interruption element 31 is designed as a continuous switching valve, which can assume a large number of intermediate positions between the first switching state and the second switching state, a virtually arbitrary valve lift curve can be displayed very flexibly under the normal valve lift curve determined by the first actuating element 15 will.
  • hydraulic medium is conducted from the hydraulic medium reservoir 37 via a bypass path 39 and a first bypass check valve 41 back into the first master cylinder 19.
  • bypass path 39 is connected to a hydraulic medium source 43 via a source check valve 45. It is possible that in this connection, in particular upstream of the source check valve 45, a filter 47 is provided.
  • Fig. 2 shows a schematic representation of a second example of a valve drive 1 for variable control of an inlet valve 3 and an outlet valve 5. Identical and functionally identical elements are provided with the same reference symbols, so that reference is made to the preceding description.
  • the inlet valve 3 and the outlet valve 5 are particularly preferably assigned to the same combustion chamber 7 of the internal combustion engine 9.
  • the outlet valve 5 is assigned a second operative connection 11 'between the valve actuation device 13, here specifically a second actuation element 15', which is also designed as a cam, the second operative connection 11 'being designed as a hydraulic operative connection and having a second hydraulic path 17' .
  • This connects a second master cylinder 19 'with a second slave cylinder 21', the second actuating element 15 'acting on the second master cylinder 19'.
  • the outlet valve 5 has a second prestressing element 23 '.
  • a second check valve 25 ' is arranged in the second hydraulic path 17', which is bypassed by a second bypass 27 'in that a second throttle element 29' is arranged.
  • the second hydraulic path 17 ' is fluidly connected - on the side of the second master cylinder 19' - to a second first inlet 33 'of a second interruption element 31', the second interruption element 31 'having a second, second fluid connection 35'.
  • the first interruption element 31 and the second interruption element 31 ′ are fluidly connected to the same hydraulic medium reservoir 37 via their second fluid connections 35, 35 ′.
  • the second interruption element 31 ' is also designed here as a switching valve, in particular as a 2/2-way valve.
  • Fig. 3 shows a schematic representation of an exemplary embodiment of the valve drive 1. Identical and functionally identical elements are provided with the same reference numerals, so that reference is made to the preceding description in this respect.
  • the first operative connection 11 and the second operative connection 11 '- apart from the variable control of the inlet valve 3 and the outlet valve 5 - function exactly as they did with reference to FIG Figures 1 and 2 has been described.
  • the activation times of the inlet valve 3 on the one hand and the outlet valve 5 on the other hand differ in time, so that precisely one interruption element 31 can be activated at a first time for variable activation of the inlet valve 3, with a second time different from the first Time for the variable control of the outlet valve 5 can be controlled.
  • the first time and the second time typically do not overlap during operation of the internal combustion engine 9, so that the one interruption element 31 can ensure full variability for both valves.
  • One interruption element 31 is connected to both the first hydraulic path 17 and the second hydraulic path 17 ′ via its first fluid connection 33.
  • the first fluid connection 33 is connected to the first hydraulic path 17 via a first interruption check valve 49, wherein the first fluid connection 33 is connected to the second hydraulic path 17 'via a second interruption check valve 49'.
  • the interruption check valves 49, 49 ' are arranged fluidically parallel to one another, in particular there is a branch from the first fluid connection 33 to the first and second interruption check valves 49, 49'.
  • the interruption check valves 49, 49 ' are each preloaded into a closed position in a direction pointing away from the first fluid connection 33 and towards the hydraulic paths 17, 17'.
  • the interruption element 31 is set up as a whole to selectively, namely in particular depending on its switching position on the one hand and the pressure levels in the hydraulic medium paths 17, 17 'on the other hand, the first hydraulic path 17, the second hydraulic path 17', or - in its second switching state - none of the hydraulic paths 17, 17 'to be brought into fluid connection with the hydraulic medium reservoir 37.
  • the internal combustion engine 9 preferably has a plurality of combustion chambers 7, in particular each of the combustion chambers 7 being assigned an inlet valve 3 and an outlet valve 5.
  • two inlet valves 3 and two outlet valves 5 can also be assigned to each of the combustion chambers 7.
  • the inlet valves 3 and the outlet valves 5 of the individual combustion chambers 7 are assigned to one another in pairs, with each valve pair - as in FIG Figure 3 shown - exactly one interruption element 31 is assigned.
  • the internal combustion engine 9 also has a control unit 51 that has a pair of valves for each associated interruption element 31 has a control means 53, in particular an output stage.
  • FIG Figure 3 In particular in contrast to the embodiment according to Figure 2 - only half the number of control means 53 for the internal combustion engine 9, because each valve pair is assigned only one interruption element 31 instead of two interruption elements 31, 31 '.
  • the control unit 51 is set up in particular to control the interruption elements 31 assigned to it at least twice per working cycle of a combustion chamber 7 assigned to the respective interruption element 31, namely once for variable control of the inlet valve 3 and a second time for variable control of the exhaust valve 5.
  • control unit 51 is set up for this does not, of course, exclude that at least one of the valves 3, 5 is not variably activated once during a working cycle, the interruption element 31 then also not being activated. It is also possible that the interruption element 31 is not activated at all in a working cycle because none of the valves 3, 5 is activated in a variable manner.
  • valve drive 1 that is fully variable on both the inlet and outlet sides can be implemented in the same installation space volume as in the case of a fully variable valve drive only on the inlet side, in that in particular a second interruption element 31 'per valve pair is omitted. This also results in a cost reduction due to a lower number of components. Furthermore, the required output stages in the control device 51 are reduced, so that costs and energy expenditure are also eliminated in this respect.

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

Claims (9)

  1. Entraînement de soupape (1) pour la commande variable d'une soupape d'admission (3) et d'une soupape d'échappement (5) d'une même chambre de combustion (7) d'un moteur à combustion interne (9), doté
    - d'une première liaison opérante (11) entre un dispositif d'actionnement de soupape (13) et la soupape d'admission (3) ;
    - d'une deuxième liaison opérante (11') entre le dispositif d'actionnement de soupape (13) et la soupape d'échappement (5), dans lequel
    - un élément d'interruption (31) est associé à la première liaison opérante (11) et à la deuxième liaison opérante (11'), lequel est disposé pour l'interruption temporaire des liaisons opérantes (11, 11'), dans lequel
    - la première liaison opérante (11) et la deuxième liaison opérante (11') sont reliées au même élément d'interruption (31) de telle sorte que
    - la première liaison opérante (11) et la deuxième liaison opérante (11') peuvent être temporairement interrompues par l'élément d'interruption (31).
  2. Entraînement de soupape (1) selon la revendication 1, caractérisé en ce que les liaisons opérantes (11, 11') sont réalisées comme liaisons opérantes hydrauliques, dans lequel l'élément d'interruption (31) est réalisé comme soupape de commutation.
  3. Entraînement de soupape (1) selon l'une des revendications précédentes, caractérisé en ce que
    - la première liaison opérante (11) comporte un premier chemin hydraulique (17) vers un premier cylindre récepteur (21), dans lequel
    - la deuxième liaison opérante (11') comporte un deuxième chemin hydraulique (17') vers un deuxième cylindre récepteur (21'), dans lequel
    - l'élément d'interruption (31) est relié au premier chemin hydraulique (17) et au deuxième chemin hydraulique (17').
  4. Entraînement de soupape (1) selon la revendication 3, caractérisé en ce que l'élément d'interruption (31) est relié au premier chemin hydraulique (17) et au deuxième chemin hydraulique (17') par le biais d'un même raccord fluidique (33).
  5. Entraînement de soupape (1) selon l'une des revendications 3 et 4, caractérisé en ce que l'élément d'interruption (31) est relié au premier chemin hydraulique (17) par le biais d'un premier clapet anti-retour d'interruption (49), dans lequel l'élément d'interruption (31) est relié au deuxième chemin hydraulique (17') par le biais d'un deuxième clapet anti-retour d'interruption (49').
  6. Entraînement de soupape (1) selon l'une des revendications 3 à 5, caractérisé en ce que l'élément d'interruption (31) est en liaison fluidique avec un réservoir de fluide hydraulique (37), dans lequel l'élément d'interruption (31) est disposé pour amener le premier chemin hydraulique (17), le deuxième chemin hydraulique (17') ou aucun des chemins hydrauliques (17, 17') en liaison fluidique avec le réservoir de fluide hydraulique (37).
  7. Moteur à combustion interne (9), doté d'un entraînement de soupape (1) selon l'une des revendications 1 à 6.
  8. Moteur à combustion interne (9) selon la revendication 7, caractérisé en ce que le moteur à combustion interne comporte une pluralité de chambres de combustion (7), dans lequel
    - à chaque chambre de combustion (7) est respectivement associée une soupape d'admission (3) et une soupape d'échappement (5), dans lequel
    - les soupapes d'admission (3) et les soupapes d'échappement (5) de chaque chambre de combustion (7) sont associées par paires l'une à l'autre en tant que paires de soupapes, dans lequel
    - à chaque paire de soupapes constituée d'une soupape d'admission (3) et d'une soupape d'échappement (5) est associé un élément d'interruption (31), dans lequel
    - le moteur à combustion interne (9) comporte un appareil de commande (51), dans lequel
    - l'appareil de commande (51) comporte un moyen de commande (53) pour chaque élément d'interruption (31) associé à une paire de soupapes.
  9. Moteur à combustion interne (9) selon l'une des revendications 7 et 8, caractérisé en ce que l'appareil de commande (51) est disposé pour commander l'élément d'interruption (31) au moins deux fois par cycle de travail de la chambre de combustion (7) associée à l'élément d'interruption (31).
EP17713160.4A 2016-04-08 2017-03-23 Dispositif de commande variable de soupape d'admission et d'échappement et moteur comprenant un tel dispositif Active EP3440323B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016205910.6A DE102016205910A1 (de) 2016-04-08 2016-04-08 Ventiltrieb zur variablen Ansteuerung eines Einlassventils und eines Auslassventils und Brennkraftmaschine mit einem solchen Ventiltrieb
PCT/EP2017/000361 WO2017174175A1 (fr) 2016-04-08 2017-03-23 Mécanisme de distribution permettant la commande variable d'une soupape d'admission et d'une soupape d'échappement, et moteur à combustion interne muni dudit mécanisme de distribution

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EP3440323B1 true EP3440323B1 (fr) 2021-01-06

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US (1) US10961878B2 (fr)
EP (1) EP3440323B1 (fr)
CN (1) CN109154215B (fr)
DE (1) DE102016205910A1 (fr)
WO (1) WO2017174175A1 (fr)

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Publication number Publication date
EP3440323A1 (fr) 2019-02-13
US10961878B2 (en) 2021-03-30
US20190120093A1 (en) 2019-04-25
CN109154215B (zh) 2021-05-18
DE102016205910A1 (de) 2017-10-12
WO2017174175A1 (fr) 2017-10-12
CN109154215A (zh) 2019-01-04

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