EP1963625B1 - Nockenwelle - Google Patents

Nockenwelle Download PDF

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Publication number
EP1963625B1
EP1963625B1 EP06828664A EP06828664A EP1963625B1 EP 1963625 B1 EP1963625 B1 EP 1963625B1 EP 06828664 A EP06828664 A EP 06828664A EP 06828664 A EP06828664 A EP 06828664A EP 1963625 B1 EP1963625 B1 EP 1963625B1
Authority
EP
European Patent Office
Prior art keywords
shaft
inner shaft
outer shaft
lateral surface
securing
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.)
Expired - Fee Related
Application number
EP06828664A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1963625A1 (de
Inventor
Falk Schneider
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP1963625A1 publication Critical patent/EP1963625A1/de
Application granted granted Critical
Publication of EP1963625B1 publication Critical patent/EP1963625B1/de
Expired - Fee Related 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
    • 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
    • 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
    • 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
    • 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 camshaft for in particular motor vehicle engines with about the camshaft axis over limited circumferential angle against each other rotatable cams according to the preamble of patent claim 1.
  • camshafts are known as adjustable or phase-adjustable camshafts. They allow a change in the timing of the gas exchange valves of an internal combustion engine.
  • camshafts are used with slidingly mounted shaft elements, wherein first cam elements are connected to an inner shaft member and second cam elements with an outer shaft member.
  • the outer shaft member to the cam elements of the inner shaft member associated with wall openings through which the cam elements with the inner shaft member connecting pins pass.
  • the cam elements of the one shaft member, the actuation of the intake valves and the cam elements of the other shaft member can control the actuation of the exhaust valves of the cylinder, whereby a valve overlap is variable, while the valve opening times are not influenced.
  • Such a camshaft is for example from the DE 39 43 426 C1 known.
  • the invention is concerned with the problem to improve a camshaft of the type mentioned in that neither during assembly of the camshaft nor during a subsequent transport thereof, a displacement of the inner shaft with respect to the outer shaft can occur.
  • the invention is based on the general idea, in a camshaft having an inner shaft and a coaxially arranged outer shaft to support the inner shaft via at least one arranged on an axial end portion of the shaft securing device directly against a stepless inner lateral surface of the outer shaft and thereby secure.
  • the stepless inner circumferential surface is formed by the formation of the outer shaft as a circular cylindrical tube with a continuous same inner diameter.
  • the at least one axial end of the inner shaft arranged securing device fixes the inner shaft radially in such a way in the outer shaft, that even under unfavorable transport conditions or during assembly of the two shafts, the coaxiality between the inner and outer shaft is maintained.
  • securing means In the axial longitudinal direction spaced from the end of the inner shaft arranged securing means is provided between an outer circumferential surface of the inner shaft and an inner circumferential surface of the outer shaft, an annular space which is filled for lubrication of the inner shaft with respect to the outer shaft, for example, with oil.
  • Two such axially arranged end side of the inner shaft securing devices allow easy insertion of mounting pins in the inner shaft, whereby the friction occurring between the mounting pins and the inner shaft does not lead to a radial displacement between the inner shaft and the outer shaft.
  • a displacement between the inner shaft and the outer shaft is reliably prevented by the safety devices even at a later transport of the camshaft.
  • the securing device has a fixedly connected to the inner shaft, annular securing element, which is arranged in the region of an axially disposed on the inner shaft end and recessed radially inwardly circumferential extent.
  • the recessed radially inward circumferential step forms a seat for the fuse element, which is firmly connected, for example via a shrink fit with the stage.
  • the fuse element can thus be connected in manufacturing technology simple manner with the inner shaft, at the same time a high manufacturing quality can be achieved or guaranteed.
  • annular sealing element Expediently axially adjacent between the peripheral stage on the one hand and the securing element on the other hand an outwardly open annular groove is formed, in which an annular sealing element is arranged, which seals the annular space between the inner and the outer shaft.
  • the annular sealing element is formed for example as an outer clamping ring and applies self-tensioning to the inner circumferential surface of the outer shaft. With its directed towards the axis of the inner shaft, radially inner region engages the annular sealing element in the annular groove and forms together with this a kind of labyrinth seal, which the annulus reliably seals between the inner and outer shaft.
  • annular surface extending in the circumferential direction and outwardly open annular groove is formed on an outer circumferential surface of the inner shaft, in which an annular securing element is provided which on the one hand supports the inner shaft against the inner lateral surface of the outer shaft and thereby secures and on the other hand also formed as a sealing element is, which seals the annulus between the inner and the outer shaft.
  • This embodiment offers the advantage of providing a combined securing and sealing element, which on the one hand material costs can be reduced by the elimination of an additional sealing element and on the other hand, the manufacturing cost can be reduced.
  • the securing element is formed physically separated from the sealing element, wherein the securing element is arranged in the same annular groove axially adjacent to the sealing element. It is also conceivable that the sealing element separately formed by the securing element is arranged in an axially spaced, second annular groove. This alternative offers the advantage that when physically separate sealing or securing elements an arrangement of the two can be adapted to individual requirements of the camshaft and thereby a more flexible handling is achieved.
  • the inner shaft axially end has a radially expanded region with which the inner shaft is secured against the inner circumferential surface of the outer shaft.
  • Such an axially widened area can for example be generated on a lathe, so that the securing device is formed integrally with the inner shaft.
  • a safety device produced in this way can be produced particularly accurately on the lathe.
  • annular groove in which a sealing element is arranged, which seals the annular space between the inner and the outer shaft.
  • Such an annular groove can also be manufactured on the lathe in one step with the manufacture of the securing device, so that not only the securing device itself, but at the same time a seat for an annular sealing element can be produced by means of the lathe.
  • other production methods such as upsetting with subsequent processing on the lathe conceivable.
  • Corresponding Fig. 1 has a camshaft 1, which is used in particular in motor vehicle engines, with the camshaft axis 2 over limited circumferential angle against each other rotatable cams 3, 4 on.
  • the mutually rotatable cam first cam 3 which are fixedly connected to an inner shaft 5 and second cam 4, which are fixedly connected to an outer shaft 6.
  • the inner shaft 5 is coaxial with and mounted within the outer shaft 6.
  • the outer shaft 6 is preferably formed as a circular cylindrical tube with a continuous same inner diameter d and thereby has a stepless inner circumferential surface 9.
  • the outer shaft 6 has for this purpose in the circumferential direction slot-like openings 8, which allow the pin 7 can be adjusted in the circumferential direction.
  • intake valves and exhaust valves of cylinders can be controlled in a known manner via cams 3 and 4 which can be adjusted to one another in this way, wherein, for example, valve overlap times can be changed while simultaneously changing the valve opening time of the intake valves.
  • the inner shaft 5 is now supported directly against the stepless inner circumferential surface 9 of the outer shaft 6 via at least one securing device 10 arranged axially on the inner shaft 5 and thereby secured.
  • the securing device 10 has a securing element 11 fixedly connected to the inner shaft 5 and configured in an annular manner, which is arranged in the region of a circumferential step 12 arranged axially on the inner shaft 5 and set back radially inward.
  • the fuse element 11 can be shrunk onto the inner shaft 5, for example by means of a shrink fit, and thereby firmly connected thereto.
  • an outwardly open annular groove 13 is formed, in which according to Fig. 1 an annular sealing element 14 is arranged, which seals an annular space 15 between the inner shaft 5 and the outer shaft 6.
  • the annular space 15 is filled with a lubricant, for example, so that a sliding mounting of the inner shaft 5 is achieved against the outer shaft 6.
  • the securing device 10 ensures the coaxiality between the inner shaft 5 and the outer shaft 6 both during insertion of the pins 7 in the inner shaft 5 and during a subsequent transport operation of the camshaft 1.
  • the coaxiality between the two shafts 5, 6 is for trouble-free operation of the camshaft 1 essential, so that the safety device 10 makes a high contribution to quality assurance.
  • the inner shaft 5 is arranged coaxially with the outer shaft 6, wherein for the attachment of the first cam 3 via the pins 7 already in Fig. 1 described should apply.
  • Fig. 1 has the securing device 10 'according to Fig. 2 a head bolt-like securing element 16, which is fixed with a portion of its shaft 17 axially end in the inner shaft 5 and which secures the inner shaft 5 against the inner circumferential surface 9 of the outer shaft 6 via an outer peripheral surface 19 of its head portion 18.
  • the shaft region 17 is connected to the inner shaft 5, for example via a press fit, and thereby fixes the securing element 11 'both in the axial direction and in the radial direction with respect to the inner shaft 5.
  • a radially outwardly open annular groove 13 ' is formed, in which according to Fig. 2 an annular sealing element 14 'is arranged, which seals the annular space 15 between the inner shaft 5 and the outer shaft 6. Also by the securing device 10 'according to the Fig. 2 Coaxiality between the inner shaft 5 and the outer shaft 6 can be ensured reliably both during assembly of the camshaft 1 and during later transport thereof.
  • a camshaft 1 is shown, in which with respect to the structure and the arrangement of the inner shaft 5, the outer shaft 6 and the cam 3 and 4 to the Fig. 1 said is referenced.
  • On an outer circumferential surface of the inner shaft 5 is according to Fig. 3 a circumferentially extending and outwardly open annular groove 13 '' formed in which an annular securing element 11 "is provided, which secures the inner shaft 5 against the inner circumferential surface 9 of the outer shaft 6.
  • the securing element 11" can either be formed as a sealing element 14 at the same time and, in addition to its securing tasks, also seal the annular clearance 15 between the inner shaft 5 and the outer shaft 6.
  • FIG Fig. 4 shown physically separate from the sealing element 14 "'and adjacent to it in the annular groove 13"' according to FIG Fig. 4 , which is then formed axially wider, be arranged. It is also conceivable for the sealing element 14 "'to be embedded in an annular groove 13""arranged adjacent to the annular groove 13"', which groove is in accordance with FIG Fig. 4 is indicated only with interrupted drawn line.
  • an axially extending channel 20 may be provided, which is formed between a bearing 24 of the outer shaft 6 and an outer circumferential surface 21 of the outer shaft 6 by a recess in the outer circumferential surface 21.
  • the channel 20 serves as a lubricant channel in order to reduce, for example, an axially end of the inner shaft 5 pending oil pressure and thereby reduce axial load on the inner shaft 5 can.
  • Such an arrangement of the channel 20 is also conceivable in the embodiments shown in the other figures, so that the illustration in Fig. 4 merely by way of example.
  • Fig. 5 has the inner shaft 5 axially end a radially expanded portion 22, with which the inner shaft 5 is secured against the inner circumferential surface 9 of the outer shaft 6.
  • the radially expanded region 22 can be produced on a lathe, in which respect, for example, an adjacent region 23 is radially tapered.
  • the annular space 15 between the outer shaft 6 and the inner shaft 5 is created.
  • the radially widened region 22 of the inner shaft 5 has an outwardly open annular groove 13 ""'. In this annular groove 13 ""'is the sealing element 14 "" and seals the annular space 15 between the inner shaft 5 and the outer shaft 6 from.
  • Each of the sealing elements 14 to 14 "" is preferably formed as an outer clamping ring and thus firmly adheres to the inner circumferential surface 9 of the outer shaft 6 and engages with its sealing lip radially inwardly into the annular groove 13 to 13 ""'of the respective embodiment according to the Fig. 1 to 5 one.
  • each of the sealing elements 14 to 14 "" with the respectively associated annular groove 13 forms a labyrinth seal and thus seals the annular space 15 reliably.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
EP06828664A 2005-12-24 2006-12-13 Nockenwelle Expired - Fee Related EP1963625B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005062207A DE102005062207A1 (de) 2005-12-24 2005-12-24 Nockenwelle
PCT/DE2006/002229 WO2007076797A1 (de) 2005-12-24 2006-12-13 Nockenwelle

Publications (2)

Publication Number Publication Date
EP1963625A1 EP1963625A1 (de) 2008-09-03
EP1963625B1 true EP1963625B1 (de) 2010-07-28

Family

ID=37905857

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06828664A Expired - Fee Related EP1963625B1 (de) 2005-12-24 2006-12-13 Nockenwelle

Country Status (5)

Country Link
US (1) US7802549B2 (pt)
EP (1) EP1963625B1 (pt)
BR (1) BRPI0620617B1 (pt)
DE (3) DE202005021716U1 (pt)
WO (1) WO2007076797A1 (pt)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011052819A1 (de) 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für Kraftfahrzeugmotoren
DE102012220652A1 (de) 2012-11-13 2014-05-15 Mahle International Gmbh Nockenwelle
EP3165721A1 (de) 2015-11-06 2017-05-10 Mahle International GmbH Nockenwelle

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226400A (ja) * 2005-02-17 2006-08-31 Jtekt Corp シャフト装置
WO2009049402A1 (en) * 2007-10-16 2009-04-23 Magna Powertrain Inc. Concentric phaser camshaft and a method of manufacture thereof
DE102009009664A1 (de) * 2009-02-19 2010-08-26 Mahle International Gmbh Nockenwelle
DE102009049218A1 (de) * 2009-10-13 2011-04-28 Mahle International Gmbh Nockenwelle für eine Brennkraftmaschine
EP2511488B1 (en) * 2009-12-07 2014-05-14 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Variable valve gear for internal combustion engine
EP2386729A1 (en) * 2010-05-10 2011-11-16 Fiat Powertrain Technologies S.p.A. Multi-cylinder internal combustion engine with variable actuation of the engine valves
DE102011052822A1 (de) * 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für Kraftfahrzeugmotoren
DE102011052823A1 (de) * 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für Kraftfahrzeugmotoren
DE102012203145A1 (de) * 2012-02-29 2013-08-29 Mahle International Gmbh Verstellbare Nockenwelle
DE102012207076A1 (de) * 2012-04-27 2013-10-31 Mahle International Gmbh Außenwelle für eine Nockenwelle und zugehöriges Herstellungsverfahren
DE102012106856B4 (de) 2012-07-27 2019-05-29 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
DE102013211159A1 (de) 2013-06-14 2014-12-31 Mahle International Gmbh Verstellbare Nockenwelle
DE102015215292A1 (de) * 2015-08-11 2017-02-16 Thyssenkrupp Ag Verfahren und Vorrichtung zur Montage einer verstellbaren Nockenwelle
DE102016224040A1 (de) * 2016-12-02 2018-06-07 Thyssenkrupp Ag Verfahren zur Montage mindestens eines Dichtringes an einer Nockenwelle in einer Lagergasse einer Verbrennungskraftmaschine, sowie eine Nockenwelle mit mindestens einem so montierten Dichtring
EP3575014A1 (de) 2018-05-28 2019-12-04 Vincenz Wiederholt GmbH Als stossdämpferrohr geeignetes zylinderrohr und verfahren zu dessen herstellung
WO2020011839A1 (en) * 2018-07-13 2020-01-16 Akzo Nobel Coatings International B.V. Tie-coat composition
USD903413S1 (en) 2018-08-09 2020-12-01 Sharkninja Operating Llc Cooking basket
EP3633157A1 (en) * 2018-10-04 2020-04-08 Mechadyne International Limited Concentric camshaft axial position control

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DE3803685A1 (de) * 1988-02-07 1989-08-17 Emitec Emissionstechnologie Nockenwelle
DE3943426C1 (pt) 1989-12-22 1991-04-11 Gkn Automotive Ag, 5200 Siegburg, De
DE4201473C2 (de) 1991-02-01 1994-06-30 Volkswagen Ag Steuervorrichtung für Ladungswechselventile einer Brennkraftmaschine mit zumindest einem desaktivierbaren Nocken auf einer Nockenwelle
JPH07102914A (ja) * 1993-03-03 1995-04-18 Peter Amborn 相互に位置決めされる軸要素を備えたカム軸構体およびその製造方法
DE9320451U1 (de) * 1993-03-03 1994-09-15 Amborn, Peter, Dr.-Ing., 53819 Neunkirchen-Seelscheid Nockenwellenanordnung mit ineinanderliegenden Wellenelementen
JPH07224617A (ja) * 1994-02-09 1995-08-22 Unisia Jecs Corp 内燃機関のバルブタイミング制御装置
DE19802484C2 (de) * 1998-01-23 2000-06-08 Daimler Chrysler Ag Verfahren und Vorrichtung zur Herstellung von gebauten Nockenwellen
DE19934405B4 (de) * 1999-07-22 2005-10-20 Daimler Chrysler Ag Hohlwelle mit Innenkanälen, insbesondere Ölkanälen
ATE331121T1 (de) 1999-12-30 2006-07-15 Thyssenkrupp Presta Ag Welle als maschinenbauteil mit integrierten leitungen
GB2369175A (en) 2000-11-18 2002-05-22 Mechadyne Plc Variable phase coupling
DE102004020124A1 (de) 2004-04-24 2005-11-17 Aft Atlas Fahrzeugtechnik Gmbh Vorrichtung zur Einstellung von Ventilsteuerzeiten sowie Brennkraftmaschine mit einer derartigen Vorrichtung
DE102005014680A1 (de) * 2005-02-03 2006-08-10 Mahle International Gmbh Nockenwelle mit gegeneinander verdrehbaren Nocken für insbesondere Kraftfahrzeuge

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011052819A1 (de) 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für Kraftfahrzeugmotoren
WO2013024140A1 (de) 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für kraftfahrzeugmotoren
DE102012220652A1 (de) 2012-11-13 2014-05-15 Mahle International Gmbh Nockenwelle
WO2014075908A1 (de) 2012-11-13 2014-05-22 Mahle International Gmbh Nockenwelle
EP3165721A1 (de) 2015-11-06 2017-05-10 Mahle International GmbH Nockenwelle
DE102015221868A1 (de) 2015-11-06 2017-05-11 Mahle International Gmbh Nockenwelle

Also Published As

Publication number Publication date
US7802549B2 (en) 2010-09-28
BRPI0620617B1 (pt) 2018-11-27
DE502006007559D1 (de) 2010-09-09
BRPI0620617A2 (pt) 2011-11-16
DE102005062207A1 (de) 2007-06-28
EP1963625A1 (de) 2008-09-03
US20100000477A1 (en) 2010-01-07
WO2007076797A1 (de) 2007-07-12
DE202005021716U1 (de) 2009-07-02

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