EP3161282B1 - Vorrichtung zur nockenwellenverstellung einer brennkraftmaschine - Google Patents

Vorrichtung zur nockenwellenverstellung einer brennkraftmaschine Download PDF

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Publication number
EP3161282B1
EP3161282B1 EP15738599.8A EP15738599A EP3161282B1 EP 3161282 B1 EP3161282 B1 EP 3161282B1 EP 15738599 A EP15738599 A EP 15738599A EP 3161282 B1 EP3161282 B1 EP 3161282B1
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EP
European Patent Office
Prior art keywords
tappet
individual
groove
control groove
tappets
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
EP15738599.8A
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German (de)
English (en)
French (fr)
Other versions
EP3161282A1 (de
Inventor
Peter Vincon
Timo Rigling
Maria GRÜNER
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.)
ETO Magnetic GmbH
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ETO Magnetic GmbH
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Publication date
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Publication of EP3161282A1 publication Critical patent/EP3161282A1/de
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Publication of EP3161282B1 publication Critical patent/EP3161282B1/de
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    • 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
    • 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
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0084—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by radially displacing the camshaft

Definitions

  • the present invention relates to a device for adjusting the camshaft of an internal combustion engine according to the preamble of the main claim, as it is known from DE 10 2011 004 912 A1 is known.
  • a generic device is from the DE 196 11 641 C1 known.
  • This document according to the prior art describes the background of the invention, including the constructive realization of the camshaft, their storage and their interaction with the internal combustion engine, which is not discussed in detail in the present application.
  • this known device as actuating means in the form of an electromagnetically driven ram unit by cooperation with a lifting profile can cause an axial, predetermined by the course of the control groove adjustment of the camshaft, such as with the purpose of assigning a cam different cam tracks switchable.
  • presupposed devices typically several plungers (actuating pins) are used so that, depending on the axial displacement position of the Hubprofilbaue, each engage a suitable the control groove against standing pin and can cause the respective intended axial displacement.
  • Nockenwellenverstellkal a provision (ie a return) of the relevant plunger but happens in that the trained with variable groove depth control back the concerning push rod back into the starting position.
  • a possible solution to this problem is to provide for the actuating means plunger units, which can be automatically (for example, again electromagnetically) spend from the driven feed position back to the restored initial position.
  • this not only causes considerable additional design effort in the realization of the actuators used for the actuating means, but in turn, in anyway limited space, such a solution again generate additional space disadvantages.
  • Object of the present invention is therefore to design a device for camshaft adjustment compact according to the preamble of the main claim and to improve in terms of reliable restoring and traceability of the plunger unit so that this, even without the need for an automatic reset and only by interaction with the Hubprofilbaueria, can be reset to a starting position, even if the Hubprofilbaueria has a compact axial extent and switching states or ram positions permits, in which - along the axial direction - an individual plunger of the plunger unit can be positioned axially outside the Hubprofilbauè.
  • the two individual plungers of the plunger unit adjacent to each other and preferably axially parallel enable at least one of the individual plungers to be positioned above or for cooperation with the control groove in each operating state so that the activation of the first individual plunger (FIG. more specifically, the activation of the preferably associated electromagnetic actuator to effect the ram feed) already creates a defined axial relationship between the ram unit and the lift profile assembly.
  • the second individual plunger in an - unintentionally and ineffective - extended (advanced) position would first by this constructive realization of the second single plunger in an axial Position in overlap with the Hubprofilbauè spent (and outside the control groove), wherein the additionally inventively formed on the Hubprofilbauxx outside the control groove radially (or alternatively also axially) height-modified (namely increased) section or the ramp section then on further rotation of the shaft (including ansitzender Hubprofilbauè) on the ramp effect then causes the resetting or driving the second single plunger.
  • the realization of the first variant of the invention with two independently controllable and drivable individual tappets ensures that even an unintentionally or incorrectly pushed forward of the individual plunger outside the control groove (which causes the proper restitution for the other, cooperating of the individual plunger) can be pushed back or reset so that then a properly located in the retracted position home plunger unit for further activations and switching operations without the risk of damaging the engine is available.
  • the second solution aspect of the invention enables the same advantageous effects;
  • the individual tappets are mechanically coupled to each other such that driving or returning one of the individual tappets automatically causes the same movement of the other of the individual tappets, so it does not need in this pairwise solution of the radially height-changed portion or the ramp portion of the first solution variant.
  • a typical implementation of a coupling according to the invention for realizing the second variant of the invention shows the DE 20 2008 008 142 U the applicant, while a possible constructive realization for the separate, independent control of the individual tappets in the exemplary WO 2008/155119 the applicant is disclosed. With regard to these constructive implementations, the disclosure contents of the cited documents are deemed to be included in the present application in each case belonging to the invention.
  • the height profile of the radially height-changed section (or of the ramp section) in such a way that it corresponds to the course of the groove depth.
  • mutually parallel and aligned individual tappets so a rectified return movement is effected in corresponding return strokes.
  • the height profile (in a developed projection of the circumference) at least in sections linearly, in this respect to ensure a uniformity in the restoring or driver movement.
  • the axial extension of the Hubprofilbau limited to a maximum of three times, preferably the maximum double and more preferably 1.5 times the distance of the individual plunger from each other (each measured by the distance of the respective plunger central axes) , Again, however, it is an advantageous development that does not limit the basic applicability of the invention to other geometric conditions.
  • the Fig. 1 illustrates first in the developed plan view of the sub-figure (b), as on a circumferential outer surface of a Hubprofilbauffle 10 (shift gate) a control groove 12 is formed along the unwound circumference (0 ° to 360 °) the shown S- or Z-shaped Groove course has.
  • This control groove 12 has the in the part of figure (a) of Fig.
  • the first embodiment of the Fig. 1 shown by hatched area 20 outside the cam groove, has a ramp portion which has a height profile (more specifically, a linearly rising slope) corresponding to the cam groove.
  • the purpose of this ramp section is the (potentially unnecessarily or erroneously extended) second single plunger P1 back to its pushed back home position to spend. This happens because of the position of the Fig.
  • the presentation of the Fig. 1 i.Ü corresponds to the representation of position 2 in Fig. 2 corresponding to the partial representations (c) and (d) and associated groove profile curves along the sections YY and XX (wherein the Fig. 2 , across from Fig. 1 in the plane of the figure shows a direction of movement 0 ° to 360 ° in the upward direction, inversely to the representation of Fig. 1 ).
  • Fig. 3 to 5 the second solution aspect of the invention by means of a second embodiment of the invention.
  • the same reference numerals illustrate the same or equivalent components, wherein the embodiment of the Fig. 3 to 5 from the embodiment of Fig. 1 . 2 differs in that at the Fig. 3-5 the pair of individual tappets P1, P2 are mechanically coupled to each other, while in the first embodiment they are independently drivable.
  • the Fig. 7 insofar as a section of the already discussed and included above DE 20 2008 008 142 U illustrates a possible constructive realization of such a coupling. Both plunger P1, P2 sit on a drive plate 28 and are held there by means of a permanent magnet 30.
  • Mit Conversely 28 and permanent magnet 30 are in turn axially in response to the energization of a coil unit 32 movable anchor components which perform in an otherwise known manner an axial lifting movement; the reference numeral 34 shows a (again otherwise known) magnetically conductive bracket section for producing a magnetic flux circuit causing the drive.
  • the arrangement thus applied according to Fig. 7 would be appropriate and as the basis for the operating behavior of Fig. 3-5 cause a simultaneous movement of both individual plunger P1, P2.
  • the second embodiment differs from Fig. 3-5 of the first embodiment in that the Hubprofilbauè (shift gate) 10 outside the cam groove 12, which is profiled itself as the cam groove 12 of the first embodiment has no ramp, but a radial (cylindrical) outer surface, the height of the deepest groove depth 16 corresponds.
  • the Hubprofilbauffle (shift gate) 10 outside the cam groove 12, which is profiled itself as the cam groove 12 of the first embodiment has no ramp, but a radial (cylindrical) outer surface, the height of the deepest groove depth 16 corresponds.
  • the example of Fig. 7 described mechanical coupling of the individual plunger P1, P2, in the course of rotation and in particular in the rising groove course 18 to the lowest groove depth of the restoring actuated single plunger P2 take outside the groove extending single plunger P1 and equally lead back into the retracted reset position.
  • the groove 12 each laterally delimiting wall portion 22 sure that on the leadership of the running in the groove plunger, a standing outside the groove plunger (eg P1 in Fig. 3 or P2 in Fig. 4 ) can not inadvertently slide into the groove, if an accidental or faulty drive this ram takes place.
  • the position 1 shown there (including partial figures (a) and (b) as well as the sections ZZ and YY) corresponds to the representations of Fig. 4 , and it matches the in Fig. 5 shown position 2 together with the subfigures (c) and (d) with section YY and XX of FIG. 3 ,
  • the sectional views, in so far simplifying, do not contain a detailed representation of the wall 22 describing the groove on both sides.
  • the embodiment of the shows Fig. 8 as an additional, generic training and development of the first embodiment of Fig. 1 . 2 a possibility not to form the ramp 20 formed outside the cam groove as a surface increasing along the circumferential direction, but as a transverse to the circumferential direction (and thus in the axial direction) extending slope 21, as the Fig. 8 in the sectional view AA illustrates the middle plan view. It becomes clear that with a slide of the plunger P1 lying here outside the groove along this axially beveled ramp 21 that the embodiment of the Fig. 1 . 2 equivalent entrainment or movement behavior can be achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Transmission Devices (AREA)
EP15738599.8A 2014-06-25 2015-06-25 Vorrichtung zur nockenwellenverstellung einer brennkraftmaschine Active EP3161282B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014108927.8A DE102014108927A1 (de) 2014-06-25 2014-06-25 Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
PCT/EP2015/064427 WO2015197777A1 (de) 2014-06-25 2015-06-25 Vorrichtung zur nockenwellenverstellung einer brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP3161282A1 EP3161282A1 (de) 2017-05-03
EP3161282B1 true EP3161282B1 (de) 2019-05-15

Family

ID=53673060

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Application Number Title Priority Date Filing Date
EP15738599.8A Active EP3161282B1 (de) 2014-06-25 2015-06-25 Vorrichtung zur nockenwellenverstellung einer brennkraftmaschine

Country Status (5)

Country Link
US (1) US10704432B2 (zh)
EP (1) EP3161282B1 (zh)
CN (1) CN106460595B (zh)
DE (1) DE102014108927A1 (zh)
WO (1) WO2015197777A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6617737B2 (ja) * 2017-03-03 2019-12-11 トヨタ自動車株式会社 内燃機関システム

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19611641C1 (de) 1996-03-25 1997-06-05 Porsche Ag Ventiltrieb einer Brennkraftmaschine
DE102007028600B4 (de) 2007-06-19 2011-06-22 ETO MAGNETIC GmbH, 78333 Elektromagnetische Stellvorrichtung
DE102008060166A1 (de) * 2008-11-27 2010-06-02 Dr.Ing.H.C.F.Porsche Aktiengesellschaft Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
DE102011004912A1 (de) * 2011-03-01 2012-09-06 Schaeffler Technologies Gmbh & Co. Kg Schiebenockensystem für Hubkolbenbrennkraftmaschinen zur Hubraumvariation von Gaswechselventilen
DE102011001125B4 (de) * 2011-03-07 2023-06-01 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb für eine Brennkraftmaschine
DE102011075537A1 (de) * 2011-05-10 2012-11-15 Schaeffler Technologies AG & Co. KG Hubkolbenbrennkraftmaschine mit Nockenwellenverstelleinrichtung
DE102012112482A1 (de) * 2012-12-18 2014-06-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verfahren zum Betreiben einer Brennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US10704432B2 (en) 2020-07-07
CN106460595A (zh) 2017-02-22
EP3161282A1 (de) 2017-05-03
CN106460595B (zh) 2019-10-18
US20180119585A1 (en) 2018-05-03
WO2015197777A1 (de) 2015-12-30
DE102014108927A1 (de) 2015-12-31

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