WO2012113424A1 - Dispositif de distribution à soupapes de moteur à combustion interne - Google Patents

Dispositif de distribution à soupapes de moteur à combustion interne Download PDF

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Publication number
WO2012113424A1
WO2012113424A1 PCT/EP2011/006069 EP2011006069W WO2012113424A1 WO 2012113424 A1 WO2012113424 A1 WO 2012113424A1 EP 2011006069 W EP2011006069 W EP 2011006069W WO 2012113424 A1 WO2012113424 A1 WO 2012113424A1
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WO
WIPO (PCT)
Prior art keywords
cam
valve
cam track
cylinder
track
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2011/006069
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German (de)
English (en)
Inventor
Thomas Stolk
Alexander Von Gaisberg-Helfenberg
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler AG filed Critical Daimler AG
Publication of WO2012113424A1 publication Critical patent/WO2012113424A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction

Definitions

  • the invention relates to an internal combustion engine valve drive device according to the preamble of claim 1.
  • From DE 102 01 932 A1 is already an internal combustion engine valve drive device with a cam member having a cam track, which is provided for actuating a valve in at least two consecutive working cycles of a cylinder and which comprises at least two working cams, which are each provided to the valve in one of the working cycles to operate, known.
  • the invention is in particular the object of increasing a flexibility of a valve operation cost. It is achieved according to the invention by the features of claim 1. Further embodiments emerge from the subclaims.
  • the invention is based on an internal combustion engine valve drive device having at least one cam element, which has at least one first cam track, which is provided for actuating a valve in at least two successive working cycles of a cylinder and which comprises at least two working cams, which are each provided to the valve in a to operate the duty cycles.
  • the cam element has at least one second cam track, which is provided for a valve drive changeover.
  • a further cam track at least two differently shaped cam tracks can be used for valve actuation, for example, have a different number of working cams and / or a different cam track course, whereby a change of the valve operation during operation of the engine valve drive device can be done only by switching between the cam tracks.
  • the changed valve actuation can take place automatically and a further actuation can be dispensed with, whereby a simple and cost-effective Internal combustion engine valve drive device can be provided. Eliminating further actuation after a valvetrain switchover can reduce loss, wear, and noise, thereby reducing fuel consumption and increasing customer satisfaction.
  • the first cam track has at least two working cam for at least two times valve actuation
  • a large number of variations of the at least one second cam track can be realized, whereby a flexibility of the valve actuation can be increased.
  • a camshaft speed can be reduced, whereby friction losses and bearing stresses can be reduced.
  • a “cam element” is to be understood in particular as meaning an element which is arranged non-rotatably on a camshaft and is provided for actuating the valve directly or indirectly to act on the valve with at least one stroke transmits a torque and / or rotational movement unchanged.
  • a “cam track” is to be understood in particular as meaning an area of the cam element running on the circumference of the cam element which forms a valve actuation curve for actuating the valve and / or which defines the valve actuation is divided into at least two articulated strokes of a piston movement in the cylinder.
  • a stroke is due to piston movement from standstill in one direction to a new stoppage, i. defined from one dead center to another dead center.
  • a cycle advantageously corresponds to half a revolution of a crankshaft.
  • a "working cam” is to be understood as meaning, in particular, a cam providing a stroke, which is necessary to provide a force-generating working cycle.
  • a “force-generating working cycle” is understood to mean, in particular, a work cycle which exerts a force on the crankshaft and is therefore fired ,
  • the force-generating duty cycle has at least one cycle in which a fuel or a fuel mixture is burned.
  • provided is intended to be understood in particular specially programmed, designed and / or equipped.
  • the second cam track is provided to operate the valve differently in the at least two consecutive working cycles.
  • a particularly advantageous valve train switching can be realized, the without activation, the valve operates differently in a repetitive rhythm in the at least two working cycles.
  • the valve train switching can be realized particularly advantageous, in which, for example, at least one duty cycle is omitted.
  • a “skipped duty cycle” is to be understood, in particular, as meaning an unfired duty cycle that does not generate force on the crankshaft and thus does no work,
  • the skipped duty cycle does not include a cycle in which the fuel or fuel mixture is burned.
  • the cam element has at least one third cam track provided for a valve drive changeover. As a result, a particularly flexible valve actuation can be provided.
  • At least one of the cam tracks is provided for an alternating shutdown or partial shutdown of at least one cylinder.
  • a cylinder deactivation operation and a valve deactivation operation can be realized particularly easily, whereby fuel consumption and friction can be reduced.
  • a charge movement can be increased, whereby combustion of the fuel or the fuel mixture can be improved.
  • a “shutdown of at least one cylinder” is to be understood as a shutdown of all valves of the at least one cylinder.
  • shutdown of at least one cylinder should be understood to mean, in particular, a shutdown of at least one valve of the at least one cylinder Valve of at least one cylinder remains active.
  • An "alternating shutdown or partial shutdown” is to be understood in particular as a shutdown or partial shutdown of a cylinder in which the cylinder is at least partially switched off in one operating cycle and the cylinder is re-fired in a subsequent operating cycle
  • the alternating deactivation or partial deactivation of the cylinder preferably takes place through the cam track, ie without actuation
  • the alternating disconnection takes place cyclically
  • a "cylinder deactivation operation” is to be understood in particular as a valve actuation , in the all valves of at least one cylinder remain unactuated and thus remain closed, whereby the cylinder is switched off.
  • valve shut-off operation should be understood to mean, in particular, a valve actuation in which at least one valve of at least two identical valves of at least one cylinder remains unconfirmed and therefore closed, whereby the cylinder is partially switched off which have the same function and are assigned to one and the same cylinder.
  • two similar valves are formed as two intake valves of a cylinder or as two exhaust valves of a cylinder.
  • the Zylinderabschalt saut governance and the Ventilabschalt safely are advantageously provided each for a low power consumption.
  • At least one of the cam tracks is provided for clock switching.
  • a combustion method can be made possible in which a duty cycle has more than four strokes, whereby a flexibility of the valve operation can be further increased.
  • the engine valve drive device comprises at least one cam element associated with a second cylinder, which has at least one cam track, which is provided for a rolling cylinder deactivation and / or a rolling valve deactivation.
  • cylinder deactivation and / or valve deactivation can independently roll without activation, as a result of which uniform wear and / or uniform heat input of the cylinders can be achieved and thus a service life of the internal combustion engine valve drive device can be increased.
  • a “rolling cylinder deactivation” is to be understood as meaning, in particular, an alternating or alternating and, in particular, cyclical disconnection between at least two cylinders.
  • a “rolling valve disconnection” is intended in particular for an alternating or alternating and in particular cyclical disconnection between at least two valves, in particular between at least two be understood similar valves.
  • the rolling cylinder deactivation and / or the rolling valve deactivation is provided by an offset on the circumference of the camshaft assembly of at least two dissimilar cam elements, whereby the corresponding valves of the different cylinders are actuated offset.
  • “dissimilar” is to be understood in particular as meaning at least two elements which have the same function and are assigned to two different cylinders. te for actuating intake valves of two different cylinders or for actuating exhaust valves of two different cylinders.
  • the internal combustion engine valve drive device has at least one cam base shaft on which the at least one cam element is arranged rotatably and axially displaceable, and it has at least one Ventiltriebumschaltü comprising at least one shift gate, which is provided for a Ventiltrieb- switching the at least one Move cam element axially on the cam base shaft.
  • a shift gate should be understood to mean a shift unit for the axial adjustment of an element which has at least one slide track which is intended to convert a rotational movement into an axial adjustment force be understood.
  • the slide track is preferably in the form of a web, in the form of a slot and / or in the form of a groove.
  • the switching pin is preferably designed in the form of a bridge shoe encompassing the web, in the form of a pin engaging in the slot and / or in the form of a pin guided in the slot.
  • the switching between the at least two cam tracks can also take place in another manner which appears appropriate to the person skilled in the art.
  • a lever such as a tilt and / or drag lever, the lever can be moved or influenced.
  • the internal combustion engine valve drive device has at least one camshaft drive unit which defines a transmission ratio between a crankshaft and the at least one cam element, which corresponds to twice the number of working cams of the first cam track. Thereby, a required speed ratio between the crankshaft and the camshaft can be found.
  • an internal combustion engine valve drive device in particular for an internal combustion engine valve drive device according to the invention, in which one valve is actuated per revolution of a cam element in two different working cycles and at least one second cam track is used for a valve drive changeover.
  • one valve is actuated per revolution of a cam element in two different working cycles and at least one second cam track is used for a valve drive changeover.
  • Fig. 6 shows a cam profile of a first cam track of a third embodiment
  • FIG. 7 shows a cam profile of a second cam track of the third exemplary embodiment.
  • FIGS 1 to 3 show schematically partially an internal combustion engine valve engine device according to the invention.
  • the internal combustion engine valve drive device is provided for a motor vehicle.
  • the internal combustion engine valve drive device has a cam base shaft 56a and a crankshaft, not shown, which are operated in this embodiment in a speed ratio of 1/4.
  • the crankshaft of the internal combustion engine valve drive device according to the invention has a speed which is four times higher than a speed of the cam base shaft 56a.
  • the engine valve drive apparatus is provided for an internal combustion engine including at least two in-line cylinders 32a, 33a, 34a, 35a having different valve operation times.
  • the internal combustion engine Ventiltrieb- device can be used for a series engine or a V-engine.
  • the internal combustion engine has four cylinders 32a, 33a, 34a, 35a arranged in series.
  • the internal combustion engine can also have another number of cylinders that appears appropriate to the person skilled in the art.
  • the internal combustion engine operates according to a four-stroke combustion process.
  • the cylinders 32a, 33a, 34a, 35a of the internal combustion engine each have a duty cycle 26a, 27a, which is divided into four cycles.
  • the cycles of a force-generating working cycle 26a, 27a are sucking, compressing, burning and expelling.
  • One cycle corresponds to half a revolution of the crankshaft.
  • a duty cycle 26a, 27a thus corresponds to two revolutions of the crankshaft.
  • the internal combustion engine having the internal combustion engine valve drive device is designed as a four-stroke engine.
  • the internal combustion engine may also be designed as a different number of cycles having engine, such as a two-stroke engine or a six-stroke engine, the duty cycle of the two-stroke engine in two cycles and the duty cycle of the six-stroke engine is divided into four cycles.
  • the cylinders 32a, 33a, 34a, 35a of the internal combustion engine further each have valves, not shown, which are provided to a combustion chamber of the corresponding cylinder 32a, 33a, 34a, 35a, in which a piston is arranged axially movable with air and / or supply air-fuel mixture and remove a burned mixture from the combustion chamber.
  • the valves are designed as intake valves and as exhaust valves.
  • the intake valves are opened at an intake stroke of the power generating duty cycle 26a, 27a of the associated cylinder 32a, 33a, 34a, 35a and the exhaust valves at an exhaust stroke of the power generating duty cycle 26a, 27a of the associated cylinder 32a, 33a, 34a, 35a.
  • the intake valves and the exhaust valves are closed at the compression stroke and the combustion stroke of the power generating duty cycle 26a, 27a of the associated cylinder 32a, 33a, 34a, 35a, respectively.
  • the cylinders 32a, 33a, 34a, 35a each have two intake valves and two exhaust valves.
  • the cylinders 32a, 33a, 34a, 35a are each formed as a four-valve in this embodiment.
  • the internal combustion engine thus has 16 valves, wherein the eight intake valves are arranged in series with one another and the eight exhaust valves are arranged in series with one another.
  • the cylinders 32a, 33a, 34a, 35a can also have a different number of valves that appears appropriate to a person skilled in the art, wherein a cylinder 32a, 33a, 34a, 35a respectively comprises at least one inlet valve and one outlet valve, which also has a different arrangement may have described above.
  • the engine valve drive device comprises two valve actuating units 60a arranged parallel to one another, wherein a valve actuating unit 60a for actuating the inlet valves and a not-shown Valve operating unit is provided for actuating the exhaust valves.
  • a valve operating unit 60a (see Fig. 1) which is provided in this embodiment for actuating the valves of the cylinders 32a, 33a, 34a, 35a formed as intake valves will be described.
  • the valve actuating unit 60a may be provided for actuating the valves designed as exhaust valves.
  • the valve actuating unit, not shown, is basically designed analogously, wherein, for example, valve actuation times of the valves may differ.
  • the valve actuating unit 60a has a cam base shaft 56a with a longitudinal axis 61a.
  • the cam base shaft 56a is connected to the crankshaft of the engine.
  • the valve operating unit 60a includes a first cam member 10a, a second cam member 11a, a third cam member 12a, a fourth cam member 3a, a fifth cam member 14a, a sixth cam member 15a, a seventh cam member 16a and an eighth cam member 17a.
  • the eight cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are arranged coaxially with one another on the cam base shaft 56a.
  • the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are each formed as a cam carrier.
  • the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a can actuate the valves in another manner that appears appropriate to a person skilled in the art, for example indirectly by means of a rocker arm, a rocker lever or the like.
  • the two similar cam elements 10a, 11a are the first cylinder 32a, the two similar cam elements 12a, 13a the second cylinder 33a, the two similar cam elements 14a, 15a the third cylinder 34a and the two similar cam elements 16a, 17a the fourth cylinder 35a assigned.
  • the cam members 0a, 11a, the cam members 12a, 13a, the cam members 14a, 15a, and the cam members 16a, 17a are adjacent, respectively, and actuate two valves of the same cylinder 32a, 33a, 34a, 35a, respectively.
  • the similar cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a thus each actuate two valves of the associated cylinder 32a, 33a, 34a, 35a.
  • the similar cam elements 10a, 11a, the similar cam elements 12a, 13a, the similar cam elements 14a, 15a, the similar cam elements 16a, 17a are each to the other similar cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a along the longitudinal axis 61a of the cam base shaft 56a offset from each other on the cam base shaft 56a arranged.
  • the cam elements 10a, 11a, the cam elements 12a, 13a, the cam elements 14a, 15a and the cam elements 16a, 17a are each offset in pairs around a circumference of the cam base shaft 56a arranged on the cam base shaft 56a, that is, two each of a cylinder 32a, 33a, 34a, 35a associated cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are to the other cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a offset in the circumferential direction. They are arranged in pairs twisted on the cam base shaft 56a.
  • the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are rotationally fixed and arranged with respect to the longitudinal axis 61a axially displaceable on the cam base shaft 56a.
  • the first cam member 10a and the second cam member 11a are integrally formed with each other.
  • the third cam member 12a, the fourth cam member 13a, the fifth cam member 14a and the sixth cam member 15a are formed integrally with each other.
  • the seventh cam member 16a and the eighth cam member 17a are formed integrally with each other.
  • the integrally formed cam elements 12a, 13a, 14a, 15a are arranged along the longitudinal axis 61a between the integrally formed cam elements 10a, 1a and the integrally formed cam elements 16a, 17a.
  • the integrally formed cam elements 10a, 11a form a first displacement element 62a, the integrally formed cam elements 12a, 13a, 14a, 15a a second displacement element 63a and the integrally formed cam elements 16a, 17a a third displacement element 64a.
  • the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a to be arranged on a separate, non-rotatably and axially displaceably arranged on the cam base shaft 56a sliding element rotationally and non-displaceably.
  • the eight cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a each have a first cam track 18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a, a second cam track 40a for a valve drive changeover.
  • the first cam member 10a associated with the first cylinder 32a, the third cam member 12a associated with the second cylinder 33a, the fifth cam member 14a associated with the third cylinder 34a, and the seventh cam member 16a associated with the fourth cylinder 35a are formed the same.
  • the second cam member 11a associated with the first cylinder 32a, the fourth cam member 13a associated with the second cylinder 33a, the sixth cam member 15a associated with the third cylinder 34a, and the eighth cam member 17a associated with the fourth cylinder 35a are made the same. They are in effect on the associated valve equal.
  • the third cam track 48a, 49a, 50a, 51a, 52a, 53a, 54a, 55a can also be dispensed with.
  • the first cam element 10a has the first cam track 18a.
  • the first cam track 18a is provided for actuating the associated valve of the first cylinder 32a.
  • the first cam track 18a is provided for operating the valve in a normal operation.
  • the first cam track 18a is provided to actuate the valve of the cylinder 32a during a single revolution of the cam member 10a in two consecutive cycles 26a, 27a of the cylinder 32a.
  • each duty cycle 26a, 27a is designed as a power-generating duty cycle.
  • the first cam track 18a has two working cams 36a, 37a, which respectively open the valve in the intake stroke of the working cycle 26a, 27a. They actuate the valve in each case in one of the two working cycles 26a, 27a.
  • a working cam 36a, 37a is provided only for one of the two working cycles 26a, 27a.
  • the working cams 36a, 37a of the first cam track 18a are provided for realizing the four-stroke combustion process to operate the valve once per cycle 26a, 27a during a single revolution of the cam member 10a. They are intended to open the associated valve during a single revolution of the cam member 10a once per working cycle 26a, 27a.
  • the working cam 36a is provided for actuating the valve in the working cycle 26a and the working cam 37a for actuating the valve in the working cycle 27a.
  • a duty cycle 26a, 27a of the cylinder 32a thus takes in each case half a revolution of the cam base shaft 56a and thus of the cam element 10a.
  • the working cams 36a, 37a of the first cam track 18a are formed as cam lobes, which provide a stroke for actuating the valve (see Fig. 2).
  • the first cam track 18a has a cam lobe and thus a working cam 36a, 37a per working cycle 26a, 27a.
  • the work cycles 26a, 27a are each formed in the normal operation by means of the first cam track 18a as a force-generating duty cycle.
  • the working cams 36a, 37a are arranged uniformly around the circumference of the cam member 10a.
  • the working cams 36a, 37a are arranged opposite one another. They have an angular distance in both circumferential directions of 180 degrees.
  • the first cam Trace 18a actuates the valve once in each cycle 26a, 27a of the cylinder 32a.
  • the first cam track 18a is duty cycle independent.
  • FIG. 2 illustrates a cam track 65a of the first cam track 18a.
  • the cam track 65a schematizes a developed first cam track 18a and a developed circumference of the first cam track 18a.
  • the cam track 65a is designed as a valve actuation curve.
  • the cam track 69a has two cam track elevations, each associated with a duty cycle 26a, 27a.
  • the cam track 65a has a length 66a of 360 degrees camshaft angle (hereinafter referred to as degree NWW).
  • degree NWW 360 degrees camshaft angle
  • a dashed line 67a indicates 180 degrees NWW.
  • the length 66a because the speed ratio between the cam base shaft 56a and the crankshaft is 1/4, corresponds to 1440 degrees crankshaft angle (hereinafter referred to as degree KWW).
  • the crankshaft rotates four times by 360 degrees.
  • the line 67a thus corresponds to 720 degrees KWW.
  • the cam track 65a associated with the duty cycle 26a and the cam track 65a associated with the duty cycle 27a have the same configuration.
  • a duty cycle 26a, 27a corresponds to 180 degrees NWW and 720 degrees KWW.
  • the first cam track 18a is provided for actuating the valve every 720 degrees KWW. It is intended to operate the valve once every two revolutions of the crankshaft.
  • the first cam track 18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a of all eight cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a is the same in operation.
  • the first cam track 19a, 20a, 21a, 22a, 23a, 24a, 25a of the seven cam elements 11a, 12a, 13a, 14a, 15a, 16a, 17a is the same as the first cam track 18a of the cam element 10a.
  • the first cam element 10a has the second cam track 40a.
  • the second cam track 40a is provided for a valvetrain changeover. It is provided for actuating the associated valve of the cylinder 32a.
  • the second cam track 40a is provided for actuating the valve in a cylinder deactivation operation.
  • the second cam track 40a is provided for alternately switching off the cylinder 32a.
  • the second cam track 40a is provided to actuate the valve of the cylinder 32a during a single revolution of the cam member 10a only in the work cycle 26a of the two consecutive cycles 26a, 27a of the cylinder 32a. In the other working cycle 27a of the cylinder 32a, the valve remains unactuated by the second cam track 40a.
  • the duty cycle 27a By an unactuated valve in the duty cycle 27a, the duty cycle 27a is discharged and the cylinder 32a for the duty cycle 27a turned off and thus operated unfired.
  • the duty cycle 27a is in the cylinder shutdown operation by means of the second cam track 40a formed as a missed cycle. In the cylinder cut-off operation, every other duty cycle 26a is formed as a power-generating duty cycle.
  • the second cam track 40a is provided for alternately switching off the associated valve of the cylinder 32a.
  • the second cam track 40a actuates the valve for alternately shutting off the cylinder 32a only in one of two cycles 26a, 27a. It leaves the valve unactuated every second cycle 27a.
  • the second cam track 40a is provided for actuating the valve every 1440 degrees KWW. It is intended to operate the valve once every four revolutions of the crankshaft.
  • the second cam track 40a is provided for working-cycle-dependent operation of the valve, in which alternately a duty cycle 27a is omitted and thereby the cylinder 32a is turned off alternately.
  • the second cam track 40a is provided for different valve actuation of the valve in the successive cycles 26a, 27a.
  • the second cam track 40a has a working cam number different from a working cam number of the first cam track 18a.
  • the second cam track 40a comprises a working cam less than the first cam track 18a, whereby the valve is actuated once per one revolution of the cam element 10a and thus per two continuous working cycles 26a, 27a.
  • the second cam track 40a turns off the valve alternately.
  • the second cam track 40a has a single operating cam 68a that opens the valve in the intake stroke in one of two cycles 26a, 27a. He operates the valve in each case in one of the two cycles 26a, 27a.
  • the working cam 68a is provided only for the working cycle 26a of the two working cycles 26a, 27a. It opens the valve in the intake stroke of the power generating duty cycle 26a.
  • the operating cam 68a of the second cam track 40a is provided for realizing the alternate cylinder deactivation of the cylinder 32a to actuate the valve only once in only the work cycle 26a of the two consecutive work cycles 26a, 27a during a single revolution of the cam member 10a. It is intended to open once the valve of the cylinder 32a during a single revolution of the cam member 10a.
  • the working cam 68a of the second cam track 40a is formed as a cam lobe providing a stroke for actuating the valve (see Fig. 3).
  • FIG. 3 illustrates a cam track 69a of the second cam track 40a, wherein the cam track course 69a likewise has the length 66a and a camshaft angle of 180 degrees is indicated by the dashed line 67a.
  • the second cam track 69a schematically illustrates a developed second cam track 40a and a developed circumference of the second cam track 40a.
  • the cam track 69a is also formed as a valve actuation curve.
  • the cam track 69a associated with the duty cycle 26a and the cam track 69a associated with the duty cycle 27a are formed differently from each other.
  • the cam track course 69a assigned to the duty cycle 26a differs from the cam track course 69a assigned to the work cycle 27a.
  • the working cam 68a is associated with the power generating duty cycle 26a.
  • the cam track 69a has a single cam lobe associated with the duty cycle 26a.
  • the skipped duty cycle 27a is assigned no working cam and thus no cam lobe.
  • the cam track 69a associated with the duty cycle 27a is configured as a zero stroke path that does not provide a stroke for actuating the valve.
  • the duty cycle 27a is assigned a zero cam.
  • the cam track 69a of the second cam track 40a associated with the duty cycle 26a corresponds to the cam track 65a of the first cam track 18a associated with the duty cycle 26a.
  • the second cam track 40a, 41a, 42a, 43a, 44a, 45a, 46a, 47a of all eight cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a is the same in operation.
  • the second cam track 41a, 42a, 43a, 44a, 45a, 46a, 47a of the seven cam elements 1a, 12a, 13a, 14a, 15a, 16a, 17a is formed the same as the second cam track 40a of the cam element 10a.
  • the first cam element 10a has the third cam track 48a for additional valve lift switching.
  • the third cam track 48a is provided for valve shut-off of the valve of the cylinder 32a. It is intended to partially shut off the cylinder 32a.
  • the third cam track 48a is provided for shutting off the valve in a valve-shutoff operation and a cylinder-part shutoff operation, respectively. It is provided for switching off the valve in all working cycles 26a, 27a of the cylinder 32a.
  • the third cam track 48a leaves the valve un-actuated.
  • the third cam track 48a is duty cycle independent.
  • the duty cycles 26a, 27a are each formed as a missed duty cycle in the valve-stop operation by the third cam track 48a. In the valve-off operation, each duty cycle 26a, 27a is formed as a missed duty cycle.
  • the third cam track 48a has no working cam. She leaves the valve closed.
  • the third cam track 48a has a cam trace formed as a valve operating curve.
  • the cam track associated with duty cycle 26a Run the third cam track 48a and the duty cycle 27a associated cam track of the third cam track 48a are formed the same.
  • the third cam track course of the entire third cam track 48a is designed as a zero stroke curve, which does not provide a stroke for actuating the valve.
  • the two working cycles 26a, 27a is assigned a zero cam.
  • the third cam track 48a of the first cam member 10a, the third cam track 50a of the third cam member 12a, the third cam track 52a of the fifth cam member 14a and the third cam track 54a of the seventh cam member 16a are similar in operation.
  • the third cam track 50a of the cam member 12a, the third cam track 52a of the cam member 14a, and the third cam track 54a of the cam member 16a are formed the same as the third cam track 48a of the cam member 10a.
  • the similar second cam member 11a has a third cam track 49a different from the third cam track 48a of the first cam member 10a, thereby achieving partial deactivation of the cylinder 32a.
  • the third cam track 49a is provided for actuating the valve of the cylinder 32a in the valve-shut-off operation.
  • the third cam track 48a of the first cam member 10a and the third cam track 49a of the second cam member 11a are provided for valve deactivation of one of the two valves of the cylinder 32a and thus for shutting off one of two intake valves of the cylinder 32a, such as at partial load ,
  • the third cam track 49a of the second cam member 1a is similar in operation to the first cam track 19a of the second cam member 1a.
  • the third cam track 49a and the first cam track 19a of the second cam element 11a are the same.
  • a cam track course of the third cam track 49a of the second cam element 11a corresponds to the cam track profile 65a of the first cam track 19a of the second cam element 1a.
  • the third cam track 49a of the second cam element 11a can also be formed in the same manner as the second cam track 41a of the second cam element 1a.
  • the third cam track 49a may also be formed differently from the first cam track 19a of the second cam element 1a, different from the second cam track 41a of the second cam element 11a and / or different from the third cam track 48a of the first cam element 10a, for example a different stroke having.
  • the internal combustion engine valve drive device has a valve drive switching unit 57a.
  • the valve drive switching unit 57a is provided for the cam elements 10a, 11a, 12a, 13a, 1a, 5a, 16a, 17a for actuating the valves of the cylinders 32a, 33a, 34a, 35a by means of one of the three cam tracks 18a-25a , 40a-47a, 48a-55a.
  • the valve train switching unit 57a is provided for switching between the three cam tracks 18a-25a, 40a-47a, 48a-55a. It is intended to position the corresponding cam track 18a-25a, 40a-47a, 48a-55a via the associated valve.
  • the valve train switching unit 57a has two shift gates 58a, 59a and two shift units 70a, 71a provided for sequentially shifting the cam elements 10a, 1a, 12a, 13a, 14a, 15a, 16a, 17a axially on the cam base 56a for valve lift switching ,
  • the switching unit 70a and the associated shift gate 58a and the switching unit 71a and the associated shift gate 59a are provided for the axial displacement of the displacement elements 62a, 63a, 64a.
  • the shift gates 58a, 59a are each formed as a groove-shaped recess.
  • a part 72a of the first shift gate 58a is integral with the cam elements 10a, 11a and another part 73a is formed integrally with the cam elements 12a, 13a, 14a, 15a.
  • the part 72a of the first shift gate 58a is integral with the shift member 62a, and the part 73a of the first shift gate 58a is formed integrally with the shift member 63a.
  • the part 72a is for the axial displacement of the cam elements 10a, 11a and the part 73a is provided for the axial displacement of the cam elements 12a, 13a, 14a, 15a.
  • a part 74a of the second shift gate 59a is formed integrally with the cam members 16a, 17a and another part 75a is formed integrally with the cam members 12a, 13a, 14a, 15a.
  • the part 74a of the second shift gate 59a is formed integrally with the shift element 64a and the part 75a is formed integrally with the shift element 63a.
  • the portion 74a of the second shift gate 59a is provided for axially displacing the cam members 16a, 17a and the portion 75a for axially displacing the cam members 12a, 13a, 14a, 15a.
  • the switching units 70a, 71a each have a switching element 76a, 77a which engages in the corresponding switching gate 58a, 59a, whereby a rotational movement of the cam base shaft 56a or the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a is converted into an axial movement of the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a.
  • the internal combustion engine valve drive device For driving the valve actuation unit 60a through the crankshaft, the internal combustion engine valve drive device has a camshaft drive unit (not shown).
  • the camshaft drive unit drives, in translation, the cam base shaft 56a of the valve operating unit 60a by means of the crankshaft.
  • the camshaft drive unit establishes a gear ratio between the crankshaft and the cam base shaft 56a corresponding to twice the number of working cams of the work cams 36a, 37a of the first cam track 18a to realize the four-cycle combustion process. It sets a gear ratio that corresponds to twice the number of working cams of a cam track 18a provided for normal operation.
  • the camshaft drive unit establishes a gear ratio between the crankshaft and the camshaft of four, whereby the crankshaft is four times faster in operation than the camshaft 56a, and thus as the cam members 10a, 11a, 12a, 13a, 14a, 15a, 16a , 17a.
  • the camshaft drive unit is designed for example as a toothed belt drive, a chain drive or a spur gear.
  • the engine valve drive apparatus has a control unit (not shown).
  • the control unit controls to set the normal operation, the Zylinderabschalt.99s and Ventilabschalt shalls the switching units 70a, 71a of the valve train switching unit 57a and thereby displaces the cam elements 10a, 1 1 a, 12a, 13a, 14a, 15a, 16a, 17a accordingly.
  • the first cam track 18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a is connected.
  • all cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are positioned with the first cam track 18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a over the associated valve.
  • All the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a actuate the corresponding valve by means of the first cam track 18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a.
  • the corresponding valves are in the normal operation with the associated cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a actuated once in each cycle 26a, 27a. They are actuated twice per cycle of cam base shaft 56a once per cycle 26a, 27a.
  • the cylinders 32a, 33a, 34a, 35a are fired in normal operation in each continuous cycle 26a, 27a.
  • the second cam track 40a, 41a, 42a, 43a, 44a, 45a, 46a, 47a is connected.
  • all the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are positioned with the second cam track 40a, 41a, 42a, 43a, 44a, 45a, 46a, 47a above the associated valve.
  • All the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a actuate the corresponding valve by means of the second cam track 40a, 41a, 42a, 43a, 44a, 45a, 46a, 47a.
  • the respective valves are actuated once in the cylinder deactivation mode with the associated cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a in every second cycle 26a.
  • the cylinders 32a, 33a, 34a, 35a are each fired alternately in the cylinder deactivation operation, every other work cycle 26a. They are alternately fired and operated unfused. Since the similar cam members 10a, 11a are offset from the similar cam members 12a, 13a, the like cam members 14a, 15a, and the like cam members 16a, 17a around the circumference of the cam base shaft 56a, the cylinder deactivation operation is performed with a rolling cylinder cutoff.
  • the four cylinders 32a, 33a, 34a, 35a are switched off alternately for one working cycle 27a, ie the cylinders 32a, 33a, 34a, 35a are switched off not continuously but alternately. If, for example, the first cylinder 32a is unfired and thus switched off, the fourth cylinder 35a is simultaneously fired, the next cylinder 26a firing the first cylinder 32a and the fourth cylinder 35a being switched off.
  • the third cam track 48a, 49a, 50a, 51a, 52a, 53a, 54a, 55a is connected.
  • all cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a are positioned with the third cam track 48a, 49a, 50a, 51a, 52a, 53a, 54a, 55a over the associated valve.
  • All the cam elements 10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a actuate the corresponding valve by means of the third cam track 48a, 49a, 50a, 51a, 52a, 53a, 54a, 55a.
  • FIGS. 4 to 7 show two further exemplary embodiments of the invention.
  • the following descriptions are essentially limited to the differences between the exemplary embodiments, reference being made to the description of the other exemplary embodiments, in particular FIGS. 1 to 3, with regard to components, features and functions that remain the same.
  • the letter a in the reference numerals of the embodiment in Figures 1 to 3 by the letters b and c in the reference numerals of the embodiments of Figures 4 to 7 is replaced.
  • identically named components in particular with regard to components with the same reference numerals, reference may in principle also be made to the drawings and / or the description of the other exemplary embodiments, in particular FIGS. 1 to 3.
  • FIGS. 4 and 5 show a cam track 78b of a first cam track 18b and a cam track 79b of a second cam track 40b of alternatively formed cam elements of an engine valve drive device according to the invention.
  • the engine driving device has a cam base shaft and a crankshaft operated in a speed ratio of 1/8 and in a speed ratio from the crankshaft to the cam base shaft of FIG. 8, respectively.
  • the crankshaft thus has a speed which is eight times higher than a speed of the cam base shaft.
  • An internal combustion engine having the internal combustion engine valve drive device operates as in the previous embodiment after a four-stroke combustion process.
  • the cam track 78b of the first cam track 18b, the cam track 79b of the second cam track 40b, and the cam track of a third cam track are different from the cam track 65a of the first cam track 18a, the cam track 69a of the second cam track 40a, and the cam track of the third cam track 48a of the previous embodiment.
  • the first cam track 18 b In order to operate the internal combustion engine in the four-stroke combustion with an eight times faster than the cam basic shaft rotating crankshaft, the first cam track 18 b, which is intended for normal operation, four working cam 36 b, 37 b, 38 b, 39 b, evenly around a circumference of Cam element are distributed (see Fig. 4). They have an angular distance in both circumferential directions of 90 degrees to each other.
  • the first cam track 18b is provided to actuate one valve during a single revolution of the cam member in four successive cycles 26b, 27b, 28b, 29b of the cylinder.
  • the four working cams 36b, 37b, 38b, 39b actuate the valve once each in four different cycles 26b, 27b, 28b, 29b.
  • Work cam 36b is associated with work cycle 26b, work cam 37b with work cycle 27b, work cam 38b with work cycle 28b, and work cam 39b with work cycle 29b.
  • the working cycles 26b, 27b, 28b, 29b are each formed in the normal operation by means of the first cam track 18b as a force-generating duty cycle. In normal operation, each duty cycle 26b, 27b, 28b, 29b is configured as a power-generating duty cycle.
  • FIG. 4 shows the cam track 78b of the first cam track 18b.
  • the first cam track 18b has a cam lobe and thus a working cam 36b, 37b, 38b, 39b per working cycle 26b, 27b, 28b, 29b.
  • the cam track 78b of the first cam track 18b has a length 66b of 360 degrees NWW.
  • a broken line 80b indicates 90 degrees NWW
  • a broken line 81b indicates 180 degrees NWW
  • a broken line 82b indicates 270 degrees NWW.
  • the length 66b corresponds to 2880 degrees KWW due to the speed ratio.
  • a duty cycle 26b, 27b, 28b, 29b corresponds to 90 degrees NWW and 720 degrees KWW, respectively.
  • a duty cycle 26b, 27b, 28b, 29b takes a quarter turn of the cam base shaft. Through a complete revolution of the cam base shaft four cycles 26b, 27b, 28b, 29b are traversed.
  • the first cam track 18b is provided for actuating the valve every 720 degrees KWW. It is intended to operate the valve once every two revolutions of the crankshaft.
  • the speed ratio between the crankshaft and the cam base shaft and the number of working cams are interdependent.
  • the speed ratio between the crankshaft and the camshaft corresponds to twice the number of working cams of the first cam member 18b.
  • the cam member has the second cam track 40b for valve train switching or valve lift switching, which has at least one working cam less than the first cam track 18b, whereby the cylinder is switched off alternately.
  • the second cam track 40b is provided for a cylinder cut-off operation.
  • the second cam track 40b is provided to allow the valve during a single revolution of the cam member only in the two cycles 26b, 27b of the four consecutive cycles 26b, 27b, 28b, 29b actuate. In the other two working cycles 28b, 29b of the four consecutive working cycles 26b, 27b, 28b, 29b, the valve remains unconfirmed by the second cam track 40b.
  • the second cam track 40b actuates the valve in two of four continuous cycles 26b, 27b, 28b, 29b.
  • the second cam track 40b actuates the valve in two consecutive cycles 26b, 27b and leaves the valve unactuated in the following two cycles 28b, 29b.
  • the cylinder is alternately fired in two successive cycles 26b, 27b and switched off in two successive cycles 28b, 29b.
  • the duty cycles 26b, 27b are respectively in the cylinder cutoff operation by the second cam lobe 40b as a force generating duty cycle, and the duty cycles 28b, 29b are respectively formed as a missed duty cycle in the cylinder cutoff operation by the second cam lane 40b.
  • two work cycles 26b, 27b are respectively formed as force-generating work cycles and two work cycles 28b, 29b are performed as missed work cycles 28b 29b.
  • the second cam track 40b has for this purpose two working cams 83b, 84b.
  • the two working cams 83b, 84b are provided for two consecutive working cycles 26b, 27b.
  • the working cam 83b is associated with the duty cycle 26b and the working cam 84b with the duty cycle 27b.
  • the work cycle 28b and the work cycle 29b is assigned no working cam.
  • the duty cycle 28b and the duty cycle 29b are each assigned a zero cam.
  • the two working cams 83b, 84b have an angular distance of 90 degrees in a circumferential direction and an angular distance of 180 degrees in an oppositely pointing circumferential direction.
  • the second cam track 40b for alternately shutting off a valve or a cylinder could have only one working cam, whereby the valve is opened only every fourth working cycle and thus the cylinder is fired only every fourth working cycle.
  • the second cam track 40b may also have three working cams, whereby the valve is opened in three successive working cycles and remains closed in one of four working cycles. The cylinder is turned off every fourth cycle.
  • the working cams 83b, 84b can, of course, also be distributed uniformly and thus have an angular spacing of 180 degrees in both mutually opposite circumferential directions, whereby the cylinder, as in the previous exemplary embodiment, every other working cycle is turned off.
  • the number of working cams and / or the angular distance between the working cams can be chosen differently, whereby, especially in combination with Nos. Ckenierin associated with other cylinders, a variety of cylinder deactivation variations can be realized.
  • the cam member has, for further valve lift switching, a third cam track, which has at least one working cam less than the first cam track 18b for alternately switching off the associated valve.
  • the third cam track is provided for alternate partial shutdown of the cylinder.
  • the third cam track is intended for a rolling valve shutdown operation. It is intended for rolling valve shutdown.
  • the third cam track and the second cam track 40b are formed identically in terms of effect.
  • a cam element assigned to the same cylinder has a third cam track arranged offset by 180 degrees about a circumference of the cam base shaft.
  • the third cam tracks of the two similar cam elements, which are each associated with a valve of the cylinder are the same design but offset from one another.
  • the valves are turned off alternately.
  • a valve of the two valves in two cycles 26b, 27b of the four working cycles 26b, 27b, 28b, 29b actuated and in two cycles 28b, 29b of the four working cycles 26b, 27b, 28b, 29b is turned off, wherein by the staggered arrangement of the actuated or unactuated valves alternate. None of the valves are switched off continuously.
  • the valves are each operated twice during the four cycles 26b, 27b, 28b, 29b and twice not operated. Rolling valve shutdown can provide even wear and prevent fuel accumulation on valves closed for extended periods of time.
  • FIGS. 6 and 7 show a cam track 85c of a first cam track 18c and a cam track 86c of a second cam track 40c of alternatively formed cam elements of an engine valve drive device according to the invention.
  • the engine valve drive apparatus has a cam base shaft and a crankshaft operated at a speed ratio of 1/6.
  • the crankshaft thus has a speed that is six times higher than a speed of the cam base shaft.
  • the cam track 85c of the first cam track 18c differs from the cam track 65a of the first cam track 18a and the cam track 78b of the first cam track 40b of the previous embodiments.
  • the first cam track 18c which is intended for normal operation, three working cam 36c, 37c, 38c, which evenly distributed around a circumference of the cam member are (see Fig. 6). They have an angular distance in both circumferential directions of 120 degrees to each other.
  • the first cam track 18c is provided for four-stroke operation of a cylinder.
  • the first cam track 18c is provided to actuate a valve during a single revolution of the cam member in three successive cycles 26c, 27c, 28c of the cylinder.
  • the three working cams 36c, 37c, 38c actuate the valve once each in three different working cycles 26c, 27c, 28c.
  • the work cam 36c is associated with the work cycle 26c, the work cam 37c with the work cycle 27c, and the work cam 38c with the work cycle 28c.
  • the working cycles 26c, 27c, 28c are each formed in the normal operation by means of the first cam track 18c as a force-generating duty cycle. In normal operation, each duty cycle 26c, 27c, 28c is configured as a power-generating duty cycle.
  • FIG. 6 shows the cam track 85c of the first cam track 18c.
  • the first cam track 18c has a cam lobe and thus a working cam 36c, 37c, 38c per working cycle 26c, 27c, 28c.
  • the cam track 85c of the first cam track 18c has a length 66c of 360 degrees NWW. Dashed line 87c indicates 120 degrees NWW and dashed line 88c indicates 240 degrees NWW. The length 66c corresponds to 2160 degrees KWW due to the speed ratio.
  • a duty cycle 26c, 27c, 28c corresponds to 120 degrees NWW and 720 degrees KWW, respectively.
  • a duty cycle 26c, 27c, 28c takes one-third of one revolution of the cam base shaft. Through a complete revolution of the cam base shaft three cycles 26c, 27c, 28c are passed through. Thus, the first cam track 18c is provided for actuating the valve every 720 degrees KWW. It is intended to operate the valve once every two revolutions of the crankshaft.
  • the cam member has a second cam track 40c for a valvetrain changeover.
  • the second cam track 40c is provided for clock switching.
  • the second cam track 40c has at least one working cam less for switching over a clocking operation, such as the first cam track 18c.
  • the second cam track 40c is provided for a six-stroke operation of a cylinder.
  • a duty cycle 30c, 31c in the six-stroke mode is divided into six cycles each.
  • the cycles of a force-generating duty cycle 30c, 31c are shown in this guide suck, compress, burn, eject, pause, pause.
  • One cycle corresponds to half a revolution of the crankshaft.
  • a duty cycle 30c, 31c thus corresponds to three revolutions of the crankshaft.
  • the force-generating working cycle 30c, 31c can also have other cycles that appear appropriate to the person skilled in the art, such as sucking in, pre-compacting, overflowing, compacting, igniting and discharging.
  • the second cam track 40c has two working cams 89c, 90c, which are arranged uniformly around a circumference of the cam element on the cam element (see FIG ). They have an angular distance in both circumferential directions of 180 degrees to each other.
  • the second cam track 40c is provided to actuate the valve during a single revolution of the cam member in two successive cycles 30c, 31c of the cylinder.
  • the two working cams 89c, 90c actuate the valve once each in two different cycles 30c, 31c.
  • the working cam 89c is associated with the duty cycle 30c and the working cam 90c with the duty cycle 31c.
  • the duty cycles 30c, 31c are each formed into a six-stroke operation by the second cam track 40c as a force-generating duty cycle. In the six-stroke operation, each duty cycle 30c, 31c is formed as a power-generating duty cycle.
  • FIG. 7 shows the cam track 86c of the second cam track 40c.
  • the cam track 86c of the second cam track 40c has a length 66c of 360 degrees NWW.
  • a dashed line 91 c indicates 180 degrees NWW and 1080 degrees KWW.
  • the duty cycles 30c, 31c correspond to 180 degrees NWW and 1080 degrees KWW, respectively.
  • a duty cycle 30c, 31c lasts for each half a revolution of the cam base shaft and three revolutions of the crankshaft. Through a complete revolution of the cam base shaft two cycles 30c, 31c are passed through, each with six strokes.
  • the second cam track 40c is provided for actuating the valve every 1080 degrees KWW. It is intended to operate the valve once per three revolutions of the crankshaft.
  • the internal combustion engine valve drive device has a control unit.
  • the control unit has a four-stroke mode for the four-stroke operation of a cylinder and a six-stroke mode for the six-stroke operation of a cylinder, in which the cylinder is fired accordingly.
  • the control unit controls to adjust of the four-stroke operation and the six-stroke operation switching units of a valvetrain switching unit and activates the corresponding mode.
  • the invention is not limited to a number of the cam elements, a number of cam tracks, a number of cylinders, a number of valves, a number of working cams, a number of working cycles, a number of cycles and / or the like limited.
  • any number of elements that appear appropriate to the person skilled in the art, in particular the above-mentioned elements, is conceivable without departing from the inventive idea of the invention.
  • any combination of the elements, in particular the above-mentioned elements, which appears expedient to the person skilled in the art, falls within the scope of protection of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

L'invention concerne un dispositif de distribution à soupapes de moteur à combustion interne, doté d'au moins un élément à cames (10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a), qui présente au moins une première trace (18a, 19a, 20a, 21a, 22a, 23a, 24a, 25a; 18b; 18c) pour cames prévue pour actionner une soupape dans au moins deux cycles de travail consécutifs (26a, 27a; 26b, 27b, 28b, 29b; 26c, 27c, 28c) d'un cylindre (32a, 33a, 34a, 35a) et qui comprend au moins deux cames de travail (36a, 37a; 36b, 37b, 38b, 39b; 36c, 37c, 38c) conçues chacune pour actionner la soupape dans un des cycles de travail (26a, 27a; 26b, 27b, 28b, 29b; 26c, 27c, 28c). Selon l'invention, l'élément à cames (10a, 11a, 12a, 13a, 14a, 15a, 16a, 17a) présente au moins une deuxième trace (40a, 41a, 42a, 43a, 44a, 45a, 46a, 47a; 40b; 40c) pour cames prévue pour une commutation de la distribution à soupapes.
PCT/EP2011/006069 2011-02-24 2011-12-03 Dispositif de distribution à soupapes de moteur à combustion interne Ceased WO2012113424A1 (fr)

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GB2519109A (en) * 2013-10-09 2015-04-15 Eaton Srl A valve train assembly
WO2016016228A1 (fr) * 2014-07-30 2016-02-04 Fev Gmbh Moteur à combustion interne à taux de compression réglable et came d'enclenchement et procédé pour faire fonctionner un moteur à combustion interne de ce type
DE102015218775A1 (de) 2015-09-29 2017-03-30 Mahle International Gmbh Brennkraftmaschine
DE102016200487A1 (de) * 2016-01-15 2017-07-20 Mahle International Gmbh Brennkraftmaschine
DE102016207716A1 (de) * 2016-05-04 2017-05-24 Continental Automotive Gmbh Nockenwelle und Vorrichtung zur Steuerung eines mehrzylindrigen Motors mit ungeradzahliger Zylinderzahl
DE102017131423B4 (de) 2017-12-29 2024-01-25 Volkswagen Aktiengesellschaft Brennkraftmaschine mit vier Zylindern und jeweils zwei Einlassventilen sowie Verfahren zum Betreiben einer solchen Brennkraftmaschine
DE102018209244A1 (de) * 2018-06-11 2019-12-12 Volkswagen Aktiengesellschaft Brennkraftmaschine mit mindestens einem Zylinder, mindestens zwei Nockenwellen und mindestens einem schaltbaren Nockenprofil

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