EP2459849A1 - Dispositif de distribution à soupapes - Google Patents

Dispositif de distribution à soupapes

Info

Publication number
EP2459849A1
EP2459849A1 EP10728139A EP10728139A EP2459849A1 EP 2459849 A1 EP2459849 A1 EP 2459849A1 EP 10728139 A EP10728139 A EP 10728139A EP 10728139 A EP10728139 A EP 10728139A EP 2459849 A1 EP2459849 A1 EP 2459849A1
Authority
EP
European Patent Office
Prior art keywords
shaft
drive device
cams
camshaft
valve drive
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.)
Granted
Application number
EP10728139A
Other languages
German (de)
English (en)
Other versions
EP2459849B1 (fr
Inventor
Tobias SCHÄDEL
Sven Skorupa
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 EP2459849A1 publication Critical patent/EP2459849A1/fr
Application granted granted Critical
Publication of EP2459849B1 publication Critical patent/EP2459849B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven 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
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to a valve drive device according to the preamble of claim 1.
  • the invention is in particular the object of providing a cost-effective valve drive device. It is achieved according to the invention by the features of claim 1. Further embodiments emerge from the subclaims.
  • the invention is based on a valve drive device, in particular an internal combustion engine valve drive device, with a first camshaft unit which has an outer shaft and primary cams connected to the outer shaft, with a second camshaft unit which has an inner shaft guided in the outer shaft and secondary cams connected to the inner shaft, and with an adjusting unit, which is intended to adjust the two camshaft units against each other.
  • a valve drive device in particular an internal combustion engine valve drive device, with a first camshaft unit which has an outer shaft and primary cams connected to the outer shaft, with a second camshaft unit which has an inner shaft guided in the outer shaft and secondary cams connected to the inner shaft, and with an adjusting unit, which is intended to adjust the two camshaft units against each other.
  • the adjustment unit is provided to provide an at least two-stage sequential valve lift switching.
  • the two-stage sequential valve lift switching an embodiment of the valve drive device for switching the primary cam and / or secondary cam can be simplified. In particular, this can reduce the costs of producing the primary cams and / or secondary cams, as a result of which a particularly cost-effective valve train system is provided. direction can be provided.
  • a "two-stage sequential valve lift changeover" should be understood to mean, in particular, a switch operation which effects a valve lift changeover in succession, in at least two steps.
  • a switching operation should be understood to mean, in particular, an axial displacement of at least one part of at least one of the camshaft units
  • the primary cams and / or secondary cams advantageously have at least two different cam curves which can be switched by axial displacement of at least one of the camshaft units and thus providing a valve lift switching.
  • At least one of the camshaft units has at least two shaft elements which are intended to be displaced sequentially one after the other in at least one switching operation. Due to the multi-part design of the inner shaft, a sequential valve lift can be realized in a simple manner.
  • the shaft elements are provided to form at least a part of the inner shaft.
  • the at least two shaft elements are connected to each other in a rotationally fixed and axially displaceable manner. This can be dispensed with a complex separate coupling of the shaft elements to a crankshaft, at the same time the sequential displacement of the multi-part running inner shaft is advantageously possible.
  • At least one of the primary cams and / or at least one of the secondary cams has at least two partial cams which are provided for the provision of different valve lifts.
  • a production of the primary cam and / or the secondary cam can be done with different cam curves particularly cost.
  • the partial cams advantageously have at least different lifting heights on, whereby a particularly advantageous valve lift switching is provided by the displacement of the primary cam and / or the secondary cam.
  • the adjusting unit comprises at least one shifting gate which is provided to axially displace at least a part of the primary cam or a part of the secondary cam in at least one operating state.
  • a "shifting gate” is to be understood in particular as an embodiment which converts a rotational movement of the shaft element into an axial force for adjusting the shaft element
  • a displacement of the shaft elements can also take place in another manner known to the person skilled in the art, for example by means of hydrodynamic, electronic and / or pneumatic actuators
  • the shifting gate is provided for the sequential displacement of the two shaft elements of the inner shaft ,
  • the shift gate is provided to at least partially couple the at least two shaft elements for sequential displacement in terms of motion technology.
  • a number of slide tracks of the shift gate can be advantageously kept low, whereby the shift gate can be constructed in an advantageously compact form.
  • the term "partially coupled in terms of motion technology" is to be understood in particular as meaning that the shifting gate is intended to couple displacement of the shaft elements via a shifting means engaging the shifting gate is provided for the sequential displacement of both shaft elements.
  • valve drive device has a form-locking unit which is provided, at least in one operating state, to connect the inner shaft and the outer shaft at least partially releasably to each other. As a result, a reliability can be ensured in a simple manner.
  • the at least two camshaft units are provided to form a combined intake and exhaust camshaft.
  • a “combined intake and exhaust camshaft” is to be understood in particular as a camshaft in which the primary cams and the secondary cams are arranged as coaxially. Nete inlet cam and exhaust cam are formed.
  • the combined intake and exhaust camshaft is designed to operate intake valves and exhaust valves. To form a combined intake and exhaust camshaft, it is particularly advantageous if the camshaft units have different valve actuation phases.
  • valve actuation phases is meant, in particular, an actuation of valves which are arranged at a defined angle to provide different opening times to each other.Two valves of a common cylinder, such as the inlet and outlet valve of a cylinder, are therefore never opened simultaneously The actuation of the valves thus always takes place in the same rhythm.
  • valve drive device has connecting elements which are intended to grip through the outer shaft and to produce a firm connection of the inner shaft with the secondary cams. Thereby, a displacement of the inner shaft, and thus the secondary cam against the outer shaft, and thus against the primary cam can be realized particularly easily.
  • the outer shaft has rectangular corner-shaped wall openings which are assigned to the secondary cams and which are provided to provide at least one axial adjustment path for valve lift switching.
  • the rectangular wall openings advantageously also provide a circumferential adjustment path for phase adjustment of the cam units relative to one another.
  • FIG. 1 shows a valve drive device according to the invention with inlet and outlet valves in a first switching position
  • Fig. 7 shows an alternative designed valve drive device for a multi-valve technology.
  • FIG. 1 shows a valvetrain apparatus designed as an engine valve drive apparatus for controlling four cylinders in series.
  • the cylinders each comprise at least one inlet valve 32a, 33a, 34a, 35a and at least one outlet valve 36a, 37a, 38a, 39a.
  • the valve train device For actuating the intake valves 32a, 33a, 34a, 35a and the exhaust valves 36a, 37a, 38a, 39a, the valve train device comprises a first camshaft unit and a second camshaft unit, which are combined with each other.
  • the first camshaft unit comprises an outer shaft 10a and primary cams 11a, 12a, 13a, 14a connected to this outer shaft 10a.
  • the second camshaft unit has an inner shaft 15a and secondary cams 16a, 17a, 18a, 19a connected to this inner shaft 15a. In this case, the inner shaft 15a is guided in the outer shaft 10a.
  • the two camshaft units form a combined intake and exhaust camshaft having, per cylinder, a valve actuation phase for the intake valves 32a, 33a, 34a, 35a and a valve actuation phase for the exhaust valves 36a, 37a, 38a, 39a.
  • Actuations of the intake valves 32a, 33a, 34a, 35a and the exhaust valves 36a, 37a, 38a, 39a are substantially different in their operation phases shifted by about 90 degrees from each other.
  • a cylinder is assigned a respective primary cam 11a, 12a, 13a, 14a and a secondary cam 16a, 17a, 18a, 19a.
  • the exhaust valve 36a, 37a, 38a, 39a of a cylinder is actuated by a primary cam 11a, 12a, 13a, 14a and the inlet valve 32a, 33a, 34a, 35a by an adjacent secondary cam 16a, 17a, 18a, 19a.
  • the valvetrain device has four primary cams 11a, 12a, 13a, 14a and four secondary cams 16a, 17a, 18a, 19a.
  • the valve drive device has an adjustment unit 22a, which comprises two functions.
  • a first function of the adjusting unit 22a is designed as a phase adjustment of the two camshaft units.
  • the adjusting unit 22a is in particular provided to set a relative phase of the two cam units to each other.
  • the adjusting unit 22a may, for example, comprise at least one adjuster, which has effective is arranged moderately between the two cam units.
  • an embodiment with two independently adjustable adjusters is conceivable, which are operatively arranged in each case between a crankshaft and one of the cam units. As adjuster wing vane adjusters can be used.
  • a second function of the adjusting unit 22a is formed as an axial displacement of the first camshaft unit relative to the second camshaft unit through which a two-stage sequential valve lift switching is provided.
  • a valve lift for the intake valves 32a, 33a, 34a, 35a can be switched over.
  • the outer shaft 10a is formed as a hollow shaft, which is non-rotatably and axially fixedly connected to the primary cam 11a, 12a, 13a, 14a (see Fig. 2).
  • the primary cams 1 1a, 12a, 13a, 14a have a cam curve which is provided for actuation of the outlet valves 36a, 37a, 38a, 39a.
  • the outer shaft 10a comprises at least one drive-side first bearing point 40a and a drive-away second bearing point 41a.
  • the first bearing 40a is provided for a fixed bearing.
  • the second bearing 41a is provided for a floating bearing. Further bearings 42a are provided between the two bearings 40a, 41a.
  • the secondary cam 16a, 17a, 18a, 19a are rotatably and axially displaceably mounted on the outer shaft 10a.
  • the guided in the outer shaft 10a inner shaft 15a is made of several parts (see Fig .. 3). It comprises a drive flange 43a operatively coupled to a crankshaft, not shown, and two shaft members 20a, 21a respectively coupled to the secondary cams 16a, 17a, 18a, 19a.
  • the secondary cams 16a, 17a, 18a, 19a each have two partial cams, each providing different cam curves. Due to the axial displacement of the inner shaft 15a, and thus also the secondary cam 16a, 17a, 18a, 19a, a valve lift is made. Due to the design of the secondary cams 16a, 17a, 18a, 19a as intake cams, in particular a valve lift for intake valves 32a, 33a, 34a, 35a of the individual cylinders is switched over during a valve lift changeover.
  • the two shaft elements 20a, 21a of the inner shaft 15a are axially displaceable and rotatably connected to each other.
  • the secondary cams 16a, 17a, 18a, 19a are coupled in pairs to one of the shaft elements 20a, 21a.
  • the second camshaft unit comprises connecting elements 23a, 24a, 25a, 26a, which are provided by the outer shaft 10a through the shaft members 20a, 21a each rotatably and axially fixed to the associated secondary cam 16a, 17a, 18a, 19a connect.
  • the connecting elements 23a, 24a, 25a, 26a are designed in this embodiment as a bolt.
  • the outer shaft 10a has wall openings 27a, 28a, 29a, 30a, through each of which one of the connecting elements 23a, 24a, 25a, 26a is passed.
  • the four wall openings 27a, 28a, 29a, 30a are rectangular.
  • the connecting elements 23a, 24a, 25a, 26a engage through the wall openings 27a, 28a, 29a, 30a in the outer shaft 10a.
  • a size of the wall opening 27a, 28a, 29a, 30a corresponds in the circumferential direction with the adjustable phase between the camshaft units. In the axial direction, the size of the wall opening 27a, 28a, 29a, 30a corresponds to an axial displacement path 60a for valve lift switching.
  • the shaft elements 20a, 21a of the inner shaft 15a are sequentially displaced sequentially by means of the adjusting unit 22a in a switching operation.
  • the adjusting unit 22a has first and second switching means which can displace the shaft elements 20a, 21a by means of a shifting gate 31a.
  • the first switching means has a first actuator and a first switching element.
  • the switching element is partially formed as a switching pin, which is extended in a switching position of the first switching element. In the switching position, the shift pin engages in a first slide track 44a of the shift gate 31a (see Fig. 4).
  • the shaft elements 20a, 21a can be moved in a first switching direction.
  • the second switching means is designed analogously. It has a second actuator and a second switching element, which is also partially formed as a Heidelbergpin on.
  • the shift pin engages in the switching position in a second slide track 45a of the shift gate 31a.
  • the slide tracks 44a, 45a by means of which the shaft elements 20a, 21a are displaced, are designed as groove-shaped depressions.
  • the shift gate 31a on two slide track elements 46a, 47a which are each firmly connected to one of the shaft members 20a, 21a.
  • the slide tracks 44a, 45a are inserted directly into the slide track elements 46a, 47a.
  • the slide track members 46a, 47a are L-shaped and axially overlapping in an area where they abut each other.
  • In the circumferential direction takes in the region of the guide tracks 44a, 45a each slide track element 46a, 47a a rotation angle of 180 ° degrees.
  • the slide tracks 44a, 45a which extend over a rotational angle greater than 360 ° degrees, are each arranged in part on the shaft member 20a and partially on the shaft member 21a.
  • Both slide tracks 44a, 45a have a basic shape with a double S-shaped structure (see FIG.
  • the slide tracks 44a, 45a each comprise a single track segment 48a, 49a for engaging the shift pins, two shift segments 50a 1 51a, 52a, 53a for sequentially shifting the slide track elements 46a, 47a and one each Ausspursegment 54a, 55a by means of which the switching elements are retracted again.
  • the switching segments 50a, 51a, 52a, 53a are each arranged completely on one of the slide track elements 46a, 47a, wherein successive shift segments 50a, 51a, 52a, 53a are arranged alternately on the slide track elements 46a, 47a.
  • the switching segments 50a, 51a, 52a, 53a and a rotational movement of the guide track elements 46a, 47a By means of the switching segments 50a, 51a, 52a, 53a and a rotational movement of the guide track elements 46a, 47a, the axial force is provided for switching the shaft elements 20a, 21a.
  • the switching segments 50a, 51a, 52a, 53a of the two cam tracks 44a, 45a are provided for different switching directions.
  • the slide track elements 46a, 47a are each firmly connected to the adjacently arranged secondary cam 17a, 18a.
  • the shaft elements 20a, 21a are partially coupled in terms of motion technology via the shifting gate 31a.
  • the shaft elements 20a, 21a can be displaced sequentially.
  • the shaft elements 20a, 21a are displaced in response to a rotation angle of the valve drive device.
  • the shaft member 21a In the first switching direction, first, the shaft member 21a is displaced, and subsequently, when the shaft member 21a is completely shifted, the shaft member 20a is displaced.
  • the second switching direction first the shaft element 20a and subsequently the shaft element 21a are displaced.
  • the shaft member 21a and the shaft member 20a are non-rotatably and axially displaceable at a coupling point P 1 , for example by means of a toothing, connected to each other. Further, at a coupling point P of the drive flange 43a also rotatably and axially displaceable, for example by means of a toothing, connected to the shaft member 20a. A torque is introduced via the drive flange 43a, transmitted via the coupling point P to the shaft element 20a and forwarded via the coupling point P 'to the shaft element 21a.
  • the two actuators which move the switching elements, each have a solenoid unit for extending the switching elements.
  • the actuators are designed as bistable systems in which the switching element remains in its position when the electromagnet unit is de-energized both in the retracted state and in the extended state.
  • the corresponding solenoid unit is energized. Retraction of the switching elements is realized by means of the slide tracks 44a, 45a.
  • the secondary cams 16a, 17a, 18a, 19a each have two partial cams, by means of which the different cam curves of the secondary cams 16a, 17a, 18a, 19a are provided.
  • the partial cams are assigned to the switching positions of the shaft elements 20a, 21a.
  • the partial cams of a secondary cam 16a, 17a, 18a, 19a, which are provided for the selective actuation of exactly one inlet valve 32a, 33a, 34a, 35a, are respectively arranged immediately adjacent to one another.
  • a base circle phase of the partial cams of a secondary cam 16a, 17a, 18a, 19a is the same in each case.
  • the switching segments 50a, 51a, 52a, 53a displace the shaft elements 20a, 21a respectively in the base circle phase of the secondary cams 16a, 17a, 18a, 19a associated with the corresponding shaft element 20a, 21a.
  • the cam curves of a secondary cam 16a, 17a, 18a, 19a differ substantially in a lifting height.
  • the small cam curves are assigned to the first switching position and have a small lifting height.
  • the large cam curves are assigned to the second shift position and have a large lift height.
  • the first part cam have a small cam curve and the second part cam a large cam curve.
  • the inlet valves 32a, 33a, 34a, 35a which are connected to a secondary cam 16a, 17a, 18a, 19a are actuated with two partial cams of different cam curves, are actuated in a first switching position of the shaft elements 20a, 21a with the partial cam of the secondary cam 16a, 17a, 18a, 19a, which has a smaller lifting height than the adjacent partial cam.
  • the shaft element 20a In the first switching position, the shaft element 20a is displaced axially as far as the stop on the drive flange 43a.
  • the shaft element 21a is axially displaced in the first switching position to the stop on the shaft element 20a (see FIG.
  • the shaft element 21a In the second switching position, the shaft element 21a is displaced axially as far as a stop of the outer shaft 10a.
  • the shaft element 20a In the second switching position, the shaft element 20a is displaced axially as far as the stop on the shaft element 21a (compare FIG. 6).
  • the inlet valves 32a, 33a, 34a, 35a are assigned the partial cams with the small stroke and in the second switching position the partial cams with the large stroke.
  • the valve drive device comprises a form-fitting unit which has two pressure pieces each assigned to one of the shaft elements 20a, 21a.
  • the pressure pieces of the form-fitting unit connect the shaft elements 20a, 21a of the inner shaft 15a releasably connected to the outer shaft 10a.
  • the outer shaft 10a has on its inner side recesses which are assigned to the switching positions and in which the fixedly connected to the inner shaft 15a plungers engage in the switching positions.
  • the form-fitting unit is formed by means of the pressure pieces as a ball latch.
  • the intake valves 32a, 33a, 34a, 35a are actuated by means of the first part cam.
  • the first switching means is switched to its switching position, whereby the first shift pin engages in the Einspursegment 48a.
  • the shape of the switching segment 50a provides an axial force by means of the rotational movement of the inner shaft 15a, which shifts the shaft element 21a and the secondary cams 18a, 19a connected to the shaft element 21a in the direction of the second bearing point 41a.
  • the shaft member 21 is thus switched to the second switching position while the operation of the intake valves 32a, 33a, which are actuated by the remaining, with the shaft member 20a coupled secondary cam 16a, 17a, remains unchanged (see Fig.5).
  • the switching operation of the shaft elements 20a, 21a is completed in half.
  • the shaft element 20a is subsequently switched into its second switching position by means of the first switching pin and the switching segment 51a, whereby the second partial cams are also connected for the secondary cams 16a, 17a coupled to the shaft element 20a (cf., FIG ).
  • the switching operation is completed by reaching the Ausspursegments 54a and the retraction of the first switching pin.
  • the valve lift switching thus takes place as a two-stage sequential valve lift switchover.
  • a switching operation from the second switching position back to the first switching position is analog, wherein the second Schalpin engages in the second slide track 45a and the shaft members 20a, 21a, starting with the shaft member 20a, are successively moved to the first switching position.
  • the switching operation in the first switching position also takes place a two-stage sequential valve lift.
  • FIG. 7 shows a further exemplary embodiment of the invention.
  • the letter a in the reference numerals of the embodiment in Figures 1 to 6 is replaced by the letter b in the reference numerals of the embodiment in Figure 7.
  • the following description is essentially limited to differences between the embodiments.
  • components, features and functions that remain the same reference may be made to the description and / or the drawings of the exemplary embodiment in FIGS. 1 to 6.
  • valve drive device designed as an internal combustion engine valve drive device for controlling four cylinders arranged in series.
  • each cylinder is assigned two intake valves and two exhaust valves.
  • the valve train device comprises a first camshaft unit and a second camshaft unit, which are combined with each other.
  • the first camshaft unit comprises an outer shaft 10b and primary cams 11b, 11b ', 12b, 12b', 13b, 13b 1 , 14b, 14b 'connected to this outer shaft 10b.
  • the second camshaft unit has an inner shaft 15b and secondary cams 16b, 16b ', 17b, 17b', 18b, 18b ', 19b, 19b' connected to this inner shaft 15b.
  • the primary cams 11b, 11b 1 , 12b, 12b 1 , 13b, 13b ', 14b, 14b' are by means of two partial cams of the same cam curves and the secondary cam 16b, 16b ', 17b, 17b', 18b, 18b ', 19b, 19b' formed by means of two partial cams of different cam curves.
  • the two camshaft units form a combined intake and exhaust camshaft having, per cylinder, a valve actuation phase for the intake valves and a valve actuation phase for the exhaust valves.
  • the outer shaft 15b is formed as a hollow shaft in which a multi-part formed inner shaft 15b is guided, wherein the inner shaft 15b of a drive flange 43b and two shaft elements 20b, 21b is constructed.
  • the drive flange 43b and the two shaft elements 20b, 21b rotatably and axially slidably connected to each other.
  • the valve drive device For rotating and shifting the camshaft units relative to one another, the valve drive device has an adjusting unit 22b.
  • the adjustment unit 22b For axial displacement of the shaft elements 20b, 21b, the adjustment unit 22b has a shift gate 31b, which axially displaces the two shaft elements 20b, 21b sequentially in two stages.
  • the primary cams 11b, 11b ', 12b, 12b', 13b, 13b ', 14b, 14b "for actuating the exhaust valves of the same cylinder are each arranged immediately adjacent and thus separate the associated secondary cam 16b, 16b', 17b, 17b ', 18b
  • the secondary cams 16b ', 17b, the secondary cams 17b', 18b and the secondary cams 18b ', 19b are also arranged immediately adjacent, the secondary cams 16b', 17b, 17b ', 18b, 18b'
  • the connecting element 56b is provided for the fixed connection of the immediately adjacent secondary cams 16b ', 17b and the connecting element 57b for the fixed connection of the immediately adjacent secondary cams 18b', 19b with the shaft element 20b, 21b.
  • the wall openings 27b, 28b, 29b, 30b, 58b, 59b rotate on the outer shaft 10b. bar and slidably mounted secondary cam 16b, 16b 1 , 17b, 17b 1 , 18b, 18b 1 , 19b, 19b 'connected by means of the connecting element fixed to the inner shaft 15b, wherein the secondary cam 16b 1 , 17b and the secondary cam 18b', 19b coupled together are.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention concerne un dispositif de distribution à soupapes, notamment un dispositif de distribution à soupapes de moteur à combustion interne, comprenant une première unité d'arbre à cames qui présente un arbre extérieur (10a; 10b) et des cames primaires (11 a, 12a, 13a, 14a; 11 b, 12b, 13b, 14b, 11 b', 12b', 13b', 14b') reliées à l'arbre extérieur (10a; 10b), une deuxième unité d'arbre à cames qui présente un arbre intérieur (15a; 15b) guidé dans l'arbre extérieur (10a; 10b) et des cames secondaires (16a, 17a, 18a, 19a; 16b, 17b, 18b, 19b, 16b', 17b', 18b', 19b') reliées à l'arbre intérieur (15a; 15b), et une unité de réglage (22a; 22b) qui sert à régler les deux unités d'arbre à cames l'une par rapport à l'autre. Selon l'invention, l'unité de réglage (22a; 22b) sert à effectuer une commutation de levée de soupape séquentielle en au moins deux étapes.
EP10728139.6A 2009-07-28 2010-06-23 Dispositif de distribution à soupapes Active EP2459849B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009034990A DE102009034990A1 (de) 2009-07-28 2009-07-28 Ventiltriebvorrichtung
PCT/EP2010/003828 WO2011012189A1 (fr) 2009-07-28 2010-06-23 Dispositif de distribution à soupapes

Publications (2)

Publication Number Publication Date
EP2459849A1 true EP2459849A1 (fr) 2012-06-06
EP2459849B1 EP2459849B1 (fr) 2019-10-09

Family

ID=42333432

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10728139.6A Active EP2459849B1 (fr) 2009-07-28 2010-06-23 Dispositif de distribution à soupapes

Country Status (6)

Country Link
US (1) US8893678B2 (fr)
EP (1) EP2459849B1 (fr)
JP (1) JP5293982B2 (fr)
CN (1) CN102472123B (fr)
DE (1) DE102009034990A1 (fr)
WO (1) WO2011012189A1 (fr)

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Also Published As

Publication number Publication date
DE102009034990A1 (de) 2011-02-03
EP2459849B1 (fr) 2019-10-09
JP2013500424A (ja) 2013-01-07
CN102472123A (zh) 2012-05-23
JP5293982B2 (ja) 2013-09-18
WO2011012189A1 (fr) 2011-02-03
US20120138000A1 (en) 2012-06-07
US8893678B2 (en) 2014-11-25
CN102472123B (zh) 2013-12-11

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