EP3332100B1 - Ventiltrieb für eine brennkraftmaschine - Google Patents

Ventiltrieb für eine brennkraftmaschine Download PDF

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Publication number
EP3332100B1
EP3332100B1 EP16751270.6A EP16751270A EP3332100B1 EP 3332100 B1 EP3332100 B1 EP 3332100B1 EP 16751270 A EP16751270 A EP 16751270A EP 3332100 B1 EP3332100 B1 EP 3332100B1
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EP
European Patent Office
Prior art keywords
cam follower
engagement element
adjustment
valve train
cam
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.)
Active
Application number
EP16751270.6A
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German (de)
English (en)
French (fr)
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EP3332100A1 (de
Inventor
Patrick Altherr
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Mahle International GmbH
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Mahle International GmbH
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Publication of EP3332100A1 publication Critical patent/EP3332100A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01L13/0005—Deactivating 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
    • 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
    • F01L1/26—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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • F01L2013/001—Deactivating cylinders
    • 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
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/101—Electromagnets
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F01L2305/02—Mounting of rollers

Definitions

  • the cylinder of an internal combustion engine can be operated in two different operating modes. If only a single cam is used instead of two cams with different lifts and - instead of a second cam - a base circle without cam lift is used, the cylinder can be switched off with the aid of the valve drive. In such a switched-off state, a cam follower coupled to a gas exchange valve of the cylinder does not interact with the single cam, but with said base circle, so that the gas exchange valve is not actuated.
  • a valve train of the type mentioned is from DE 199 45 340 A1 known. Also from the JP 2014 224496 A , the EP 2 487 341 A1 , the DE 10 2009 005731 A1 , the US 2014/190432 A1 , the WO 2010/136875 A1 and the US 2014/165940 A1 such adjustable valve trains are known.
  • the basic idea of the invention is accordingly to equip a valve drive with a purely mechanical adjusting device, by means of which the cam follower can be adjusted between a first and a second axial position.
  • a valve train according to the invention comprises a camshaft and a cam follower.
  • a first cam and, axially adjacent to it, a second cam are attached to the camshaft in a rotationally fixed manner.
  • An axial direction can be defined by the central longitudinal axis of the camshaft.
  • the first cam can be arranged axially at a distance from the first cam or bear against it.
  • the cam follower is axially adjustable along an axial direction.
  • the cam follower is axially adjustable between a first position in which the cam follower is drivingly connected to the first cam and a second position in which the cam follower is drivingly connected to the second cam.
  • the cam follower has a mechanical adjustment device which interacts with the camshaft for the axial adjustment of the cam follower between the first and the second position.
  • the mechanical adjusting device has an adjustable first mechanical engagement element. For the axial adjustment of the cam follower from the first to the second position, this interacts with at least one first link guide present on the camshaft.
  • the adjusting device also has a second mechanical engagement element that can be produced and which, for the axial adjustment of the cam follower from the second to the first position, interacts with at least one second link guide present on the camshaft.
  • the mechanical adjustment device comprises a first actuator.
  • the first actuator By means of the first actuator, the first mechanical engagement element can be adjusted between a first position in which it engages the first link guide and a second position in which it can be adjusted does not intervene in the first link guide.
  • the mechanical adjustment device comprises a second actuator, by means of which the second mechanical engagement element can be adjusted between a first position in which it engages the second link guide and a second position in which it does not engage the second link guide.
  • the first actuator can be adjusted between an inactive position and an active position.
  • the adjustability can preferably be implemented such that the first actuator is out of contact with the first engagement element in the inactive position and the first engagement element is moved from the inactive position to the active position through mechanical contact from the second to the first Adjusted position.
  • the second actuator can also be adjustable between an inactive position and an active position as an alternative or in addition to the first actuator.
  • the second actuator is also out of contact with the second engagement element in the inactive position. By moving from the inactive position to the active position, the second actuator moves the second engagement element from the second to the first position by mechanical contact.
  • the first and / or second engagement element is adjusted from the first to the second position with the aid of the lifting movement of the cam follower.
  • the cam follower is moved towards the two actuators by the lifting movement caused by the first or second cam. If these are in their active position, the lifting movement of the cam follower and thus the respective engagement element pressed the respective engagement element against the respective stationary, ie immovable, actuator in the active position relative to the camshaft, and in this way "shifted" the actuator into its second position.
  • An active adjustment of the first or second engagement element by an active movement of the first or second actuator can be dispensed with in this way. Accordingly, the two actuators can be constructed very simply, which leads to cost advantages in production.
  • the adjustment of the first engagement element from the first to the second position can also take place at least partially by means of an active movement of the first actuator from the inactive position to the active position.
  • the adjustment of the second engagement element from the first to the second position can take place at least partially by means of an active movement of the second actuator from the inactive position to the active position.
  • a third cam is present in the valve drive in addition to the first and the second cam, so that the cam follower can be adjusted between a first, a second and a third position.
  • the two first link guides can expediently be essentially parallel and at a distance from one another on a first link body.
  • the two second link guides can be arranged essentially parallel and at a distance from one another on a second link body.
  • the three cams are also arranged axially between the two link bodies. This variant requires particularly little axial installation space.
  • one of the two first link guides is designed for adjusting the cam follower from the first to the second position.
  • the other first link guide is designed to move the cam follower from the second position to the third position.
  • one of the two second link guides is designed for adjusting the cam follower from the third back to the second position.
  • the other, second link guide is designed to adjust the cam follower from the second position back into the first position.
  • the two link guides are axially adjustable relative to the camshaft and are connected to the cam follower by means of a coupling element.
  • Said coupling is implemented in such a way that an axial movement of the link guides for adjustment between the first and second positions is accompanied by an identical axial movement of the cam follower.
  • a particularly long service life of the mechanical adjustment device is associated with this design variant.
  • the two link guides preferably the at least one sleeve, part of a bearing device comprising bearing elements, are particularly useful.
  • the camshaft is rotatably supported by such a bearing device, for example on a housing part of the valve train or on another component of the valve train. This variant is also associated with a reduced space requirement and a reduced weight of the entire valve train.
  • the coupling element engages in a recess provided on the sleeve.
  • the recess which is preferably implemented as a circumferential groove formed on the outer circumference of the sleeve.
  • the coupling element can be designed like a bolt or pin and protrude radially outward from the cam follower. This variant requires particularly little installation space.
  • the two actuators can particularly preferably be designed as linearly adjustable, electrically driven actuators. In this case, they can be controlled in a simple manner by a control device of the valve drive for adjusting between the active position and the inactive position.
  • implementation as electrical actuators allows very precise control of the linear positioning of the actuators along their direction of adjustment.
  • the mechanical adjustment device is implemented as an electromechanical adjustment device.
  • the first actuator has a linearly adjustable first adjusting element.
  • This can comprise a cylindrical adjusting body, the end face of which presses against an end face of the engagement element opposite the first adjusting element when the first engagement element is moved into the first link guide.
  • the second actuator can also have a linearly adjustable second actuating element which is cylindrical Has adjusting body. Its end face can, in a manner analogous to the first adjusting element, press against an end face of the second engagement element opposite the second adjusting element when the second engagement element is moved into the second link guide.
  • the desired mechanical coupling of the actuator to the engagement element can be implemented in a simple and thus inexpensive manner.
  • the first actuator has a housing and a first adjusting element which is translationally adjustable relative to the housing between the first and the second position.
  • the second actuator as an alternative or in addition to the first actuator, can also have a housing and a second adjusting element which is translationally adjustable relative to this housing between the first and the second position.
  • the first and second link guides are formed in a common link body which is arranged axially on the same side of a cam follower role of the cam follower relative to the two cams.
  • the cam follower has a cam follower fixing device for releasably fixing the cam follower in the first or second position.
  • the cam follower fixing device has a spring-loaded cam follower fixing element. In the first position of the cam follower, this engages in a first receptacle provided on the cam follower and in the second position of the cam follower in an am Cam follower provided a second recording.
  • the first receptacle is designed as a first circumferential groove formed on the circumferential side of the cam follower.
  • the second receptacle is designed accordingly as a second circumferential groove arranged axially at a distance from the first circumferential groove on the circumferential side.
  • the cam follower expediently has an engagement element fixing device for releasably fixing the engagement element in the first or second position.
  • said engagement element fixing device has a spring-loaded fixing element. This is received in the first position of the engagement element in a first receptacle provided on the engagement element. In the second position of the engagement element, the fixing element is received in a second receptacle provided on the cam follower.
  • the first and / or second engagement element preferably each have a bolt-like or pin-like base body, on the circumferential side of which the first receptacle is designed as a first circumferential groove and the second receptacle is designed as an axially spaced second circumferential groove.
  • the mechanical adjustment device does not include any hydraulic and / or pneumatic components.
  • the first or second cam is to be designed as a base circle without a cam lift.
  • the invention further relates to an internal combustion engine with a valve drive presented above.
  • the Figures 1 and 2 illustrate in a schematic representation an example of a valve drive 1 according to the invention.
  • the valve drive 1 comprises a camshaft 2 and a cam follower.
  • a first cam 4a is attached to the camshaft 2 in a rotationally fixed manner.
  • a second cam 4b is arranged axially adjacent to the first cam 4a on the camshaft 2, likewise non-rotatably with respect to this.
  • the first cam 4a is designed as a base circle without a cam lift. This allows the valve drive 1 to be used in an internal combustion engine with a cylinder that can be switched off.
  • the cam follower is adjustable along an axial direction A between a first position, in which it is drivingly connected to the first cam 4a, and a second position, in which it is drivingly connected to the second cam 4b.
  • Figure 1 shows the cam follower in said first position
  • Figure 2 shows the cam follower in its second position.
  • the cam follower can have a cylindrical cam follower base body 5 whose circumferential side is a hollow cylindrical cam follower roller 6 is rotatably mounted.
  • the cam follower base body 5 is also known to the person skilled in the art under the designation “bolt” or “displacement axis”.
  • the drive connection of the two cams 4a, 4b to the cam follower takes place in a known manner via the cam follower roller 6.
  • the rotary movement of the camshaft 2 is converted into a linear movement of the cam follower by means of the cams 4a, 4b.
  • the cam follower roller 6 is coupled to the first cam 4a shown in the first position of the cam follower shown in FIG Figure 2 with the second cam 4b.
  • the cam follower roller 6 controls (not shown) via a suitably designed mechanical coupling device, in particular in the form of an actuator, a valve for adjusting between an open and a closed state.
  • a suitably designed mechanical coupling device in particular in the form of an actuator, a valve for adjusting between an open and a closed state.
  • the cam follower of the Figure 1 has a mechanical adjusting device 7 which interacts with the camshaft 2 for the axial adjustment of the cam follower between the first and the second position.
  • the mechanical adjusting device 7 comprises a first adjustable mechanical engagement element 8a.
  • the first mechanical engagement element 8a acts to axially adjust the cam follower from FIG Figure 1
  • the mechanical adjusting device 7 has an adjustable second mechanical engagement element 8b.
  • the second engagement element 8b interacts with a second link guide 9b present on the camshaft for the axial adjustment of the cam follower from its second to the first position.
  • a hardened steel can be used as the material for the camshaft 2, which can be surface-hardened, in particular nitrided, in the area of the two link guides.
  • the mechanical adjustment device 7 further comprises a first actuator 10a, by means of which the first engagement element 8a between an in Figure 1 first position shown, in which it engages in the first link guide 9a, and one in Figure 2 second position shown is adjustable, in which it does not engage in the first link guide 9a.
  • the mechanical adjustment device 7 also comprises a second actuator 10b, by means of which the second engagement element 8b can be adjusted between a first position in which it engages the second link guide 9b and a second position in which it does not engage in said second link guide 9b.
  • the first actuator 10a can be adjusted between an inactive position and an active position.
  • the two actuators 10a, 10b can be designed as linearly adjustable, electrically driven actuators.
  • the mechanical adjusting device 7 is implemented as an electromechanical adjusting device in this case.
  • electrically driven actuators 10a, 10b are encompassed by the term “mechanical control device” 7 in the present case.
  • the two actuators 10a, 10b can be controlled by a control device 11 of the valve drive 1 for adjustment between their active position and their inactive position. This adjustability is realized such that the first actuator 10a is out of contact with the first engagement element 8a in the inactive position. In the course of an adjustment from its inactive position to its active position, the first actuator 10a adjusts the first engagement element 8a from its second to its first position by mechanical contact.
  • the adjustment of the first engagement element 8a from the first to the second position can preferably be effected by means of the lifting movement of the cam follower, in particular by means of the cam follower base body 5.
  • the cam follower is moved in the direction of the first actuator 10a by the stroke movement caused by the first or second cams 4a, 4b. If the latter is in its active position, the lifting movement of the cam follower and thus of the first engagement element 8a press the latter against the first actuator 10a and move it into its second position.
  • the adjustment of the first engagement element 8a from the first to the second position can also take place while executing a synchronized active movement of the first actuator 10a from the inactive position to the active position.
  • the first engagement element 8a engages in the first link guide 9a, so that the cam follower is moved axially from its first to the second position due to the rotary movement of the camshaft 2 with the aid of the first link guide 9a arranged thereon.
  • the second actuator 10b can also be adjusted between an inactive position and an active position. This adjustability is realized such that the second actuator 10b is out of contact with the second engagement element 8b in the inactive position. In the course of an adjustment from its inactive position to its active position, the second actuator 10b adjusts the second engagement element 8b from its second to its first position by mechanical contact.
  • the adjustment of the second engagement element 8b from the first to the second position is also preferably effected by means of the lifting movement of the cam follower, in particular by means of the cam follower base body 5.
  • the cam follower is moved in the direction of the second actuator 8b by the lifting movement caused by the first or second cams 4a, 4b. If this is in its active position, Thus, by the lifting movement of the cam follower and thus of the second engagement element 8b, the latter is pressed against the second actuator 10b and thus displaced by the latter into its second position.
  • the adjustment of the second engagement element 8b from the first to the second position can also take place while executing a synchronized active movement of the first actuator 10a from the inactive position to the active position.
  • the second engagement element 8b engages in the second link guide 9b, so that the cam follower is moved axially from its second to the first position due to the rotary movement of the camshaft 2 with the aid of the second link guide 9a arranged on it.
  • the first actuator 10a has a linearly adjustable (cf. arrow 15a) first adjusting element 12a. This can partially protrude from a first housing 16a of the first actuator 10a and be arranged linearly adjustable relative to this.
  • An end face 13a of the first actuating element 12a facing the first engagement element 8a which can be designed like a pin or bolt, presses against an end face 14a of the first engagement element 8a opposite the first actuating element 12a when the first engagement element 8a is moved into the first link guide 9a.
  • the second actuator 10b has a linearly adjustable (cf. arrow 15b) second adjusting element 12b. This can partially protrude from a second housing 16b of the second actuator 10b and be arranged linearly adjustable relative to this.
  • a face 13b of the second actuating element 12b facing the second engagement element 8b presses when the second engagement element 8b is moved into the second link guide 9b against an end face 14b of the second engagement element 8b opposite the second actuating element 12b.
  • the cam follower also has a cam follower fixing device 17 for releasably fixing the cam follower in FIG the first or second position.
  • the cam follower fixing device 17 comprises a spring-loaded cam follower fixing element 18.
  • the cam follower fixing element 18 engages in a first receptacle 19a provided on the cam follower in the first position of the cam follower and engages in a second receptacle 19b provided on the cam follower in the second position of the cam follower on.
  • the first receptacle 19a is preferably as in FIG Figure 2 realized as a first circumferential groove 20a, which is arranged on a circumferential side 21 of the cam follower.
  • the second receptacle is implemented accordingly as a second circumferential groove 20b arranged axially at a distance on the circumferential side 21.
  • the cam follower for the two engagement elements 8a, 8b preferably for both engagement elements 8a, 8b, each has a first and second engagement element fixing device 22a, 22b for releasably fixing the first and second engagement element 8a, 8b in the first or second engagement element second position.
  • the two engagement element fixing devices 22a, 22b each have a spring-loaded fixing element 23a, 23b, which in the first position of the respective engagement element 8a, 8b is received in a first receptacle 24a, 24b provided on the respective engagement element 8a, 8b.
  • the fixing element 23a, 23b is received in a second receptacle 25a, 25b provided on the cam follower.
  • the first and the second engagement element 8a, 8b each have a bolt-like or pin-like base body 29a, 29b.
  • the first receptacle 24a, 24b is designed as a first circumferential groove 27a, 27b and the second receptacle 25a, 25b as a second circumferential groove 28a, 28b arranged axially at a distance on the circumferential side.
  • the first engagement element 8a of the mechanical adjustment device 7 is as in FIG Figure 1 shown brought into engagement with the first link guide 9a. This is done with the aid of the first electrical actuator 10a.
  • the first actuator 10a is between one in Figure 1 shown inactive position and an active position - in Figure 1 indicated by dashed lines adjustable.
  • the first actuator 10a In the inactive position, the first actuator 10a is mechanically out of contact with the first engagement element 8a.
  • the first actuator 10a adjusts the first engagement element 8a from its second to its first position by mechanical contact.
  • the first engagement element 8a engages in the first link guide 9a (cf. Figure 1 ), so that the cam follower is moved axially from its first to its second position by the rotary movement of the camshaft 2 with the aid of the first link guide 9a, which is shown in Figure 2 is shown.
  • the first actuator 10a can be moved back into its inactive position by the control device 11.
  • the first link guide 9a can - like the second link guide 9b - have a ramp structure, not shown in the figures, such that the first engagement element 8a is disengaged from the first link guide as soon as the cam follower has reached the second axial position.
  • the second cam 4b is in drive connection with the cam follower roller 6.
  • the adjustment of the cam follower from the second position back to the first position can be done with the help of the second actuator 10b, the second engagement element 8b and the second link guide 9b in a manner analogous to previously explained transition from the first to the second position of the cam follower take place.
  • valve drive can also be designed in such a way that not the entire cam follower but only the cam follower role of the cam follower is axially adjusted between the first and the second position.
  • the link guides 9a, 9b can each be formed on a first or second sleeve 42a, 42b. At least one of the two sleeves 42a, 42b - in the example of Figures 1 and 2 the second sleeve 42b can be part of a bearing device 46.
  • the storage device 46 comprises in the Figures 1 and 2 Conventional bearing elements 47a, 47b, indicated only roughly schematically, by means of which the camshaft 2 is rotatably supported on a housing (not shown) or another stationary component of the valve drive 1.
  • Figure 3 is a variant of the example of the Figures 1 and 2 shown.
  • the valve train 1 of the Figure 3 differs from that of the Figures 1 and 2 in that the first and second link guides 9a, 9b are formed axially on the same side in a common link body 26 relative to the two cams 4a, 4b. It is clear that this is accompanied by a change in the axial arrangement of the two engagement elements 8a, 8b and the two link guides 9a, 9b and the two actuators 10a, 10b.
  • the variant of the Figure 3 requires very little installation space in the axial direction A.
  • Figure 4 is another variant of the example of the Figures 1 and 2 shown, where in Figure 4 the camshaft 2 and the cam follower are shown only in an axial partial section for the sake of clarity.
  • the two link guides 9a, 9b relative to the camshaft 2 axially adjustable mounted on this and by means of a coupling element 41 with the Cam follower connected.
  • Said coupling is implemented in such a way that a movement of the link guides 9a, 9b along the axial direction A for adjusting the cam follower between the first and second positions is also accompanied by an axial movement of the cam follower.
  • the coupling element 41 is as in FIG Figure 4 shown is bolt-like or pin-like and protrudes radially outward from the cam follower.
  • the two link guides 9a, 9b are designed as outer circumferential grooves 45a, 45b on a common sleeve 42.
  • Said sleeve 42 is axially displaceable (see arrow 20 in Figure 4 ) pushed onto camshaft 2.
  • the coupling element 41 for mechanical axial coupling can engage in a recess 43 provided on the sleeve 42, which as in FIG Figure 4 indicated is preferably realized as a circumferential groove 44 formed on the outer circumference of the sleeve 42.
  • the Figure 5 shows a further variant of the example of FIG Figures 1 and 2 , in which on the camshaft 2 not only two cams, but three cams 4a, 4b, 4c are non-rotatably arranged.
  • valve train 1 of the Figure 5 the cam follower is consequently adjustable between a first, a second and a third position.
  • the cam follower roller 6 interacts with the third cam 4c.
  • Figure 5 shows the Figure 5 the cam follower roller 6 in engagement with the second cam 4b.
  • FIG. 5 further shows, there are not only a single first link guide 9a and a single second link guide 9b in the valve drive 1, but each two first link guides 9a and two second link guides 9b are present.
  • the two first link guides 9a are arranged essentially parallel and at a distance from one another on a first link body 40a.
  • the two second link guides 9b are arranged essentially parallel and at a distance from one another on a second link body 40b.
  • the three cams 4a, 4b, 4c are arranged axially between the two link bodies 40a, 40b on the camshaft 2.
  • One of the two first link guides (9a) is used to move the cam follower from its first position to its second position.
  • the other first link guide 9a is used to adjust the cam follower from the second position to its third position.
  • one of the two second link guides 9b is used to adjust the cam follower from the third position back into the second position.
  • the other second link guide 9b is used accordingly to adjust the cam follower from the second position to the first position.
  • the Figures 6 and 7 illustrate an advantageous further development of the valve drive 1 when it is used to control valves.
  • the example of the Figures 6 and 7 can with the above using the Figures 1 to 5 illustrated examples.
  • Figure 6 shows an adjusting lever 30 rotatably mounted on a housing (not shown in detail) about an axis of rotation S in a side view along the axial Direction A.
  • the adjusting lever 30 is adjusted by a movement of the cam follower of the valve drive 1.
  • Two valve bodies 31a, 31b are fixedly attached to the adjusting lever 30.
  • the two valve bodies 31a, 31b close or release a valve opening 32a, 32b assigned to them as a function of the currently set position of the adjusting lever 30.
  • the two valve bodies 31 a, 31 b can be adjusted between a closed position and an open position by means of the adjusting lever 30.
  • the Figure 6 shows the two valve bodies 31a, 31b in their open position.
  • the Figure 7 shows the valve train 1 of Figure 6 in a plan view of the two valve openings 32a, 32b.
  • the adjusting lever 30 is designed to be adjustable along the axial direction A and can be adjusted together with the cam follower between a first and a second position.
  • the adjusting lever 30 has a first lever arm 33a and a second lever arm 33b.
  • the first valve body 31a is arranged on the first lever arm 33a, the second valve body 31b on the second lever arm 33b.
  • the first valve body 31a is designed by suitable dimensioning in such a way that it closes the valve opening 32a in its closed position regardless of whether the cam follower and thus also the actuating lever 30 are in the first or second position.
  • the other valve body - in the example of Figure 7 so the second valve body 31b - is designed such that it has the valve opening 32a in its The closed position only closes when the cam follower and thus the control lever 30 are in the first or, alternatively, in the second position.
  • valve bodies 31a, 31b In the example of Figure 7 the cam follower and adjusting lever 30 are in the second position, so that in their closed position both valve openings 32a, 32b are closed by valve bodies 31a, 31b.
  • the first valve body 31a has a greater extent or expansion along the axial direction A than the second valve body 31b.
  • FIG Figure 7 With the first position set in the cam follower for the two valve bodies 31a, 31b, this scenario is in FIG Figure 7 indicated in dashed lines:
  • the first valve body 31a sits a greater extent or expansion along the axial direction A than the second valve body 31b.
EP16751270.6A 2015-08-07 2016-08-05 Ventiltrieb für eine brennkraftmaschine Active EP3332100B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE202015009047.8U DE202015009047U1 (de) 2015-08-07 2015-08-07 Ventiltrieb für eine Brennkraftmaschine
DE102016204893.7A DE102016204893A1 (de) 2015-08-07 2016-03-23 Ventiltrieb für eine Brennkraftmaschine
PCT/EP2016/068799 WO2017025478A1 (de) 2015-08-07 2016-08-05 Ventiltrieb für eine brennkraftmaschine

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EP3332100A1 EP3332100A1 (de) 2018-06-13
EP3332100B1 true EP3332100B1 (de) 2021-01-27

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US (1) US10641136B2 (zh)
EP (1) EP3332100B1 (zh)
CN (1) CN108368753B (zh)
DE (2) DE202015009047U1 (zh)
WO (1) WO2017025478A1 (zh)

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US20180230862A1 (en) 2018-08-16
DE202015009047U1 (de) 2016-08-03
DE102016204893A1 (de) 2017-02-09
US10641136B2 (en) 2020-05-05
CN108368753A (zh) 2018-08-03
CN108368753B (zh) 2020-11-10
WO2017025478A1 (de) 2017-02-16
EP3332100A1 (de) 2018-06-13

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