EP2396522B1 - Ventiltrieb einer brennkraftmaschine - Google Patents

Ventiltrieb einer brennkraftmaschine Download PDF

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Publication number
EP2396522B1
EP2396522B1 EP10704501.5A EP10704501A EP2396522B1 EP 2396522 B1 EP2396522 B1 EP 2396522B1 EP 10704501 A EP10704501 A EP 10704501A EP 2396522 B1 EP2396522 B1 EP 2396522B1
Authority
EP
European Patent Office
Prior art keywords
cam
section
axial
excursion
groove
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.)
Not-in-force
Application number
EP10704501.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2396522A1 (de
Inventor
Harald Elendt
Lars PFÜTZENREUTER
Axmacher Detlef
Andreas Nendel
Markus Schnepp
Mathias Boegershausen
Heiko Schmidt
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to PL10704501T priority Critical patent/PL2396522T3/pl
Publication of EP2396522A1 publication Critical patent/EP2396522A1/de
Application granted granted Critical
Publication of EP2396522B1 publication Critical patent/EP2396522B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L2301/00—Using particular materials
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/12—Fail safe operation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49293—Camshaft making

Definitions

  • the invention relates to a valve train of an internal combustion engine, comprising a carrier shaft and a rotatably mounted thereon and slidably disposed between two axial cam piece comprising at least one cam group immediately adjacent cams with different cam lobes and a Axialkulisse with two axially peripherally
  • Axialkulisse actuator for moving the cam piece in the direction of both cam tracks.
  • Such a valve train which is used for variable actuation of gas exchange valves by means of sliding cam and in which a single actuator per cam piece is sufficient to move the cam piece in the direction of both cam tracks of Axialkulisse is considered from the considered generic DE 101 48 177 A1 previously known.
  • There two cam pieces are disclosed with alternatively designed Axialkulissen, wherein the first Axialkulisse has a central guide bar to form inner guide walls for the actuator in the form of a dipping into the Axialkulisse cylindrical pin and the second Axialkulisse consists only of outer guide walls.
  • the latter embodiment has the advantage that the production cost for the axial slide is significantly smaller due to the omission of the guide bar.
  • a considerable risk in terms of the reliability of the valve train in this embodiment is that the displacement of the cam piece is completed completely, ie without a fault, if the mass inertia of the cam piece is sufficient to pass it through the crossing region of the curved paths without force of the cylinder pin to a certain extent in free flight to move to its other end position.
  • a prerequisite for the sufficient inertia of the cam piece is of course a minimum speed of the camshaft, which directly from the friction between the cam piece and the Carrier shaft is dependent.
  • a displacement of the cam piece rotating below this minimum rotational speed can cause the cam piece to stop "halfway" and a cam follower acting on the gas exchange valve to be acted upon by several cams of the cam group uncontrolled and under high mechanical loads simultaneously.
  • a valve train having the features of the preamble of claim 1 is also known from DE 101 48 178 A1 and the DE 10 2007 037 232 A1 out.
  • the present invention is therefore the object of a valvetrain of the type mentioned in such a way that the said functional limitations and risks are at least partially eliminated.
  • the object is therefore, when using a single actuator for both Verschieberungen even at low speeds of the camshaft, for example during the starting process of the internal combustion engine, a successful, i. ensure complete switching of the cam piece.
  • the curved paths should be arranged one behind the other in the circumferential direction of the axial slide.
  • a significant difference of the invention over the prior art thus relates to the mutual arrangement of the curved paths on the Axialkulisse, which now consecutively, ie in series, and no longer next to each other, ie in parallel, run and therefore no longer intersect. Due to the omission of the crossing region, the displacement of the cam piece takes place under permanent forced guidance of the axial slide against the actuating element coupled thereto, so that a complete switching operation of the cam piece is ensured even at the lowest rotational speeds of the camshaft.
  • the cam tracks are each formed as a groove and the actuating element as engaging in the grooves cylindrical pin.
  • the curved paths are each of successive track sections composed with different axial strokes of the groove bounding groove walls, namely an entry section without Axialhub, a ramp section and a lifting section, wherein the lifting section has a significantly greater axial acceleration than the ramp section.
  • the cams should have a common base circle area, which begins at the latest with the ramp portion of the first curved path and ends at the earliest with the lifting portion of the second curved path. Since the common base circle region is to be understood as the angular range of the cam piece in which all the cams of the cam group are free of elevation, the displacement of the cam piece takes place only when the gas exchange valve associated with the cam group is closed and the cam to be engaged during the entire displacement operation also located in its base circle position. Thus, during the displacement process, no valve spring forces increasing the friction between the cam piece and the carrier shaft act on the cam piece. In order to keep the axial acceleration of the cam piece as small as possible, the beginning and the end of the base circle area and of the shifting process are ideally identical.
  • the lifting sections may each be composed of successive Operahubabitesen with different radial strokes of the groove delimiting groove base, namely a first Operahubabites without radial stroke and a second Operahubabites with radially outwardly uplifting groove bottom.
  • the actuating pin is "ejected" only in axialkraft laminate state from the radially rising groove in its non-engaging rest position
  • the cam angle of the lifting sections can be maximized for a given length of the intermediate section.
  • FIG. 1 a section of a variable valve train of an internal combustion engine essential for the understanding of the invention is disclosed.
  • the valve train points a camshaft 1, which a carrier shaft 2 and - the number of cylinders of the internal combustion engine accordingly - rotatably thereto and slidably disposed between two axial positions cam pieces 3 comprises.
  • the carrier shaft 2 are provided with an outer longitudinal toothing and the cam piece 3 with a corresponding inner longitudinal toothing.
  • the teeth are known per se and not shown here.
  • the cam piece 3 has on both sides of a bearing 4 arranged cam groups, each with two immediately adjacent cams 5 and 6, which have different cam elevations at the same base circle radius.
  • the displacement of the cam piece takes place outside the cam elevations during the common base circle region of the cams 5, 6.
  • the cam elevations are each in a known manner by a cam follower symbolized here only by a cam roller 7, e.g. a drag lever, selectively transmitted in dependence on the instantaneous axial position of the cam piece 3 to a gas exchange valve, not shown.
  • the different cam elevations are to be understood as meaning different amounts of the respective cam lift and / or different valve control times of the cams 5, 6.
  • the cam piece 3 is provided with a manufactured as a single part and joined by means of interference fit Axialkulisse 8.
  • Axialkulisse 8 On the circumference of the Axialkulisse 8 are two axially oppositely extending and circumferentially of the Axialkulisse 8 successively arranged cam tracks 9, 10 are formed in the form of grooves, in which an actuating element 11 can be coupled.
  • the actuating element 11 is a cylindrical pin, which is part of a likewise known actuator, which is not explained here, for such valve trains.
  • the cylinder pin 11 is axially fixed relative to the camshaft 1, but arranged radially displaceable in the internal combustion engine and serves to move the cam piece 3 in the direction of both cam tracks 9, 10th
  • FIGS. 1 to 6 The design of the curved paths 9, 10 results from a synopsis of FIGS. 2 to 6 .
  • the in the FIGS. 2 to 4 shown views on the axial slide 8 correspond to the view arrows x, y and z in FIG. 5 in which the axial slide 8 shown in side view is additionally provided with a radial control diagram of the cam tracks 9, 10 according to the dashed line.
  • the in the FIGS. 1, 2 and 5 Arrows indicated represent the direction of rotation of the camshaft 1.
  • a complete lift diagram with radial and axial stroke of the cam tracks 9, 10 as a function of the camshaft angle goes out FIG. 6 out.
  • the two cam tracks 9, 10 each consist of successive track sections with different axial strokes (solid line in FIG FIG. 6 ) of the groove bounding groove walls 12 together.
  • These track sections are an entry section F or C without axial stroke, a ramp section A or D for compensating axial position tolerances of the cylindrical pin 11 relative to the groove walls 12 and a lift section B or E, wherein the axial acceleration of the lift sections B, E is significantly greater than that of the ramp sections A, D.
  • the common base circle area of the cams 5, 6 is identical to the track sections A to E, ie the common base circle area begins with the ramp section A of the first cam track 9 and ends with the Lifting section E of the second curved path 10.
  • the cam elevations of the cams 5, 6 are in the region of the entry section F.
  • the lifting sections B and E are each composed of successive Operahubabrisken B1 and B2 or E1 and E2, which in the radial stroke of the groove bottom 13 (dashed line in FIGS. 5 and 6 ).
  • the first Operahubabriske B1 and E1 a groove bottom 13 with constant and identical to the sections F and A and C and D depth, while the groove base 13 rises radially outwardly over the second Operahubabriske B2 and E2 to the cylinder pin 11 already eject during the sliding operation of the cam piece 3 from the respective groove in its non-engaging rest position.
  • the switching of the cam piece 3 along the first cam track 9, ie from the currently active cam 5 on the cam 6 see FIG.
  • the locking device comprises two in a formed as a through hole radial bore 14 of the support shaft 2 diametrically opposed, slidably mounted locking body 15 and the inner circumference of the cam piece 3 extending, as circumferential grooves formed locking grooves 16 and 17, in which the force-loaded by a spring means 18 in radially outward direction locking body 15 are engaged in the respective associated axial positions.
  • the locking bodies 15 are unilaterally open, thin-walled Blechumformmaschine.
  • the open side is each as mounted in the radial bore 14 and formed as a helical compression spring spring means 18 enclosing hollow cylinder, while it is in the subsequent closed side each in the direction of the locking grooves 16, 17 tapered hollow body, the first conical and the front side is spherical.
  • the locking body 15 are provided in the conical portion of the hollow body with a pressure relief opening 19.
  • the function of the locking device is not limited to the fixation of the cam piece 3 in the two axial positions, but also includes a braking of the cam piece 3 in its axial movement towards the end of Operahubabitese B2 and E2.
  • This braking is generated by contact friction of the spring-loaded locking body 15 on the both sides of the apex point 20 axially adjacent groove walls of the locking grooves 16, 17.
  • the locking grooves 16, 17 are geometrically identical and the vertex 20 - based on the distance of the locking grooves 16, 17 associated axial positions of the cam piece 3 - runs centrally.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP10704501.5A 2009-02-14 2010-02-01 Ventiltrieb einer brennkraftmaschine Not-in-force EP2396522B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10704501T PL2396522T3 (pl) 2009-02-14 2010-02-01 Rozrząd zaworowy silnika spalinowego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009009080A DE102009009080A1 (de) 2009-02-14 2009-02-14 Ventiltrieb einer Brennkraftmaschine
PCT/EP2010/000582 WO2010091798A1 (de) 2009-02-14 2010-02-01 Ventiltrieb einer brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP2396522A1 EP2396522A1 (de) 2011-12-21
EP2396522B1 true EP2396522B1 (de) 2015-06-17

Family

ID=41720375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10704501.5A Not-in-force EP2396522B1 (de) 2009-02-14 2010-02-01 Ventiltrieb einer brennkraftmaschine

Country Status (8)

Country Link
US (1) US8584639B2 (pl)
EP (1) EP2396522B1 (pl)
KR (1) KR101602989B1 (pl)
CN (1) CN102282341B (pl)
DE (2) DE202009015465U1 (pl)
HU (1) HUE025402T2 (pl)
PL (1) PL2396522T3 (pl)
WO (1) WO2010091798A1 (pl)

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DE102013204655A1 (de) 2013-03-18 2014-09-18 Schaeffler Technologies Gmbh & Co. Kg Ventiltrieb eines Verbrennungsmotors
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JP5928835B2 (ja) 2013-07-03 2016-06-01 株式会社デンソー バルブリフト調整装置
CN103437894B (zh) * 2013-08-13 2017-03-22 奇瑞汽车股份有限公司 发动机停缸控制装置及控制方法
KR101448784B1 (ko) * 2013-08-27 2014-10-10 현대자동차 주식회사 다단 가변 밸브 리프트 장치
DE102013111476B4 (de) * 2013-10-17 2021-09-09 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb einer Brennkraftmaschine
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DE102013223299A1 (de) 2013-11-15 2015-05-21 Schaeffler Technologies AG & Co. KG Schiebenockensystem mit verlängertem Einspurbereich
US9482122B2 (en) * 2014-06-30 2016-11-01 GM Global Technology Operations LLC Detent assembly and a method of assembling the detent assembly
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KR102119446B1 (ko) * 2014-11-14 2020-06-05 현대자동차 주식회사 다단 가변 밸브 리프트 장치
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DE102015204041A1 (de) * 2015-03-06 2016-04-14 Schaeffler Technologies AG & Co. KG Schiebeachsenventiltrieb einer Brennkraftmaschine
US9518644B1 (en) * 2015-05-26 2016-12-13 GM Global Technology Operations LLC Sliding camshaft with improved compressive residual stress
DE102015219106A1 (de) * 2015-10-02 2017-04-06 Bayerische Motoren Werke Aktiengesellschaft Vorrichtung zum axialen Verstellen eines Schaltelementes
DE112016004372T5 (de) 2015-11-06 2018-06-07 Borgwarner Inc. Ventilbetätigungssystem, das einen variablen ventilhub und/oder variable ventilzeitsteuerung bereitstellt
DE102017210281B4 (de) * 2016-06-21 2021-12-09 Thyssenkrupp Ag Mehrstufig zu schaltende Schiebenockeneinrichtung
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CN111720186B (zh) * 2020-07-13 2023-09-01 中船动力有限公司 柴油机气阀旋转装置
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Also Published As

Publication number Publication date
US8584639B2 (en) 2013-11-19
PL2396522T3 (pl) 2015-11-30
HUE025402T2 (en) 2016-02-29
KR101602989B1 (ko) 2016-03-11
KR20110124236A (ko) 2011-11-16
DE202009015465U1 (de) 2010-02-25
US20110247577A1 (en) 2011-10-13
CN102282341A (zh) 2011-12-14
CN102282341B (zh) 2014-08-20
EP2396522A1 (de) 2011-12-21
DE102009009080A1 (de) 2010-08-19
WO2010091798A1 (de) 2010-08-19

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