EP1844216B1 - Verstellbare nockenwelle, insbesondere für verbrennungsmotoren von kraftfahrzeugen, mit einer hydraulischen stelleinrichtung - Google Patents

Verstellbare nockenwelle, insbesondere für verbrennungsmotoren von kraftfahrzeugen, mit einer hydraulischen stelleinrichtung Download PDF

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Publication number
EP1844216B1
EP1844216B1 EP06705778A EP06705778A EP1844216B1 EP 1844216 B1 EP1844216 B1 EP 1844216B1 EP 06705778 A EP06705778 A EP 06705778A EP 06705778 A EP06705778 A EP 06705778A EP 1844216 B1 EP1844216 B1 EP 1844216B1
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EP
European Patent Office
Prior art keywords
bearing ring
ring
channels
shafts
section
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
EP06705778A
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German (de)
English (en)
French (fr)
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EP1844216A1 (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
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Mahle International GmbH
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Publication date
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Publication of EP1844216A1 publication Critical patent/EP1844216A1/de
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Publication of EP1844216B1 publication Critical patent/EP1844216B1/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
    • 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
    • F01L13/0057—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 splittable or deformable cams
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift

Definitions

  • the invention relates to an adjustable camshaft, in particular for internal combustion engines of motor vehicles, with a hydraulic actuating device according to the preamble of patent claim 1.
  • camshafts with hydraulic actuators are known in terms of the supply of hydraulic fluid in a variety of designs. Only by way of example may be mentioned here JP 7286507 A . DE 198 20 063 A1 . DE 199 62 981 A1 . DE 196 45 688 A1 . DE 196 15 076 A1 . DE 195 25 837 A1 . DE 100 20 119 A1 . DE 695 12 962 T2 ,
  • JP 7286507 A should supply the necessary to operate the hydraulic actuator hydraulic fluid in a constructive and moderately simple construction require the smallest possible space.
  • the invention is based in particular with respect to camshafts of internal combustion engines in motor vehicles on the general idea of using the pressure oil lubrication required for the bearing ring, including the means serving for this purpose, at the same time to supply the adjusting device with lubricating oil as the hydraulic fluid.
  • the camshaft consists in this area of an outer shaft 1 and a concentrically mounted in this inner shaft 2.
  • adjustable camshafts of an internal combustion engine of a motor vehicle.
  • adjustable camshafts are located on the outer shaft 1 each firmly connected to this first cam.
  • Second cams are fixedly connected to the inner shaft 2 in a rotatable mounting on the outer shaft 1.
  • the fixed connection between the second cam and the inner shaft 2 takes place through recesses in the outer shaft 1 therethrough.
  • This adjusting device 5 comprises two relatively mutually rotatable adjusting elements, namely a first adjusting element 6 and a second adjusting element 7.
  • first adjusting element 6 with the bearing ring 3 and the second adjusting element 7 with the inner shaft 2 are respectively firmly connected.
  • the connection is such that, in the case of both adjusting elements 6, 7, a contact is made with an end-side end region of the inner shaft 2, the outer shaft 1 and the bearing ring 3 fixedly connected thereto.
  • end face connecting surfaces which are defined together as the connecting surface 8.
  • feed channels 9 to 12 To supply the hydraulic adjusting device 5 a total of four feed channels 9 to 12 are provided in the illustrated embodiment.
  • the areas of these feed channels 9 to 12, which are located outside of the adjusting device 5, are each indicated without a line index, while the portions which are located within the actuator, each having a prime index are occupied.
  • the number of feed channels 9 to 12 depends on the structure and the function that an adjusting device 5 is to exercise.
  • Four feed channels 9 to 12 are required in particular in known embodiments of adjusting devices 5, if in addition to a relative movement between the inner and outer shaft 2, 1, the entirety of both shafts 1, 2 with respect to a stationary storage should be adjustable in angle.
  • the supply channel 9 extends outside of the adjusting device 5 exclusively in the bearing ring 3 and communicates from there via an end-side connecting surface 8 with an associated feed channel 9 'in the first adjusting element 6 of the adjusting device 5.
  • the feed channel 9 opens at one end axially parallel to the camshaft in the Connecting surface 8 and the other end radially into an annular channel 9 "in the outer peripheral surface of the bearing ring 3.
  • the preparation of this Zulitekanales 9 takes place by crossing blind holes from one side of the connecting surface 8 and on the other hand from the annular channel 9" starting.
  • the annular channel 9 is supplied from a in the abutment 4 associated inlet channel 9" 'with hydraulic fluid, that is, here in the described embodiment with lubricating oil under pressure.
  • feed channel 10 directly adjacent feed channel 10 extends in turn between the connecting surface 8 and an annular channel 10 "on the outer peripheral surface of the bearing ring 3.
  • the lubricating oil supply of this Zucrystallinekanales 10 takes place in the same manner as that of the feed channel 9 described above.
  • the feed channel 10 is not composed of blind hole bores crossing within the bearing ring 3. Rather, the feed channel 10 consists of a radial bore, which passes through the entire radial thickness of the bearing ring 3 and a radial annular gap 10 IV between the outer shaft 1 and the bearing ring 4.
  • the annular gap 10 IV is on the connecting surface 8 and through it within the Adjustment 5 a feed channel 10 'associated with communicating flow. Through the annular gap 10 IV , the bearing ring 3 sits firmly on the outer shaft 1 exclusively via its axially adjacent this annular gap 10 IV area.
  • the feed channel 11 is similar in construction and course to the feed channel 10 described above. Also, this feed channel 11 opens via an annular channel 11 IV in an associated feed channel 11 'on the connecting surface 8 away in the adjusting device 5 inside. To connect the annular channel 11 IV with the radially extending portion of the feed channel 11 is a guided through the outer shaft 1 radial bore 11 V is used .
  • the feed channel 12 has, like the feed channel 11 within the bearing ring 3, a radial bore which opens into an intersecting blind hole bore within the inner shaft 2 via an associated radial through hole 12 V of the outer shaft 1.
  • the axially extending region of these blind bores of the feed channel 12 leads out via the connecting surface 8 away in a corresponding feed channel 12 'within the actuator 5.
  • the inner shaft 2 can be provided up to its axial end within the camshaft with a large outer diameter, whereby a good torsional rigidity is obtained.
  • a plurality of feed channels can be provided, each of which can be controlled individually. The arrangement of the feed channels in particular enables an axial force-free row of hydraulic fluid supply to the actuating device 5.
  • the difference in the design of the feed channel 209 results exclusively from a different design the associated end portion of the camshaft, wherein the inner shaft 2 extends axially on the one hand axially beyond the associated end of the outer shaft 1 and on the other hand is stepped diametrically to a section with a smaller diameter.
  • the outer bearing ring 3 "and the inner bearing ring 3 ' may be made of different materials, each adapted to the requirements placed on these areas. while the inner bearing ring portion 3 'can be formed of high strength material to absorb and transmit the driving forces.
  • the feed channels can be executed milled in a split bearing ring design, at least in some areas, which can be compared to purely drilled feed channels easier to produce direction-changing courses. In particular, a large number of small holes can be combined to form a necessary larger flow cross-section, if a larger diameter hole can not be realized in terms of space.
  • the bearing ring 3 may be finished prior to assembly on a camshaft, that is, the outer shaft 1, which has a positive effect on the manufacturing time, cost and quality.
  • bearing ring designs which are described in detail below, are those which can be used particularly advantageously in the context of the present invention. Basically, however, these are bearing ring designs that can be used anywhere regardless of an adjustable camshaft according to the present invention in such cases in which liquid from lying on the outer circumference of a bearing ring ring channels through the bearing ring is to be performed at axially adjacent ring channels and a possible axially short training of the bearing ring.
  • a bearing ring 30 has on its outer circumference axially adjacent annular channels 31, the functionally the annular channels 9 ", 10", 11 “and 12" in the execution of the bearing ring 3 after Fig. 1 correspond.
  • radial bores 32 lead into the inner peripheral surface of the bearing ring 30.
  • Individual of the annular channels 31 contain sealing rings 33, one of which bears against each of the two axial flanks of these annular channels 31.
  • the sealing rings 33 provide for a bearing of the bearing ring 30 in an abutment in, for example, an embodiment of that of the abutment 4 in Fig. 1 for a mutually dense demarcation of the annular channels 31. Due to the above-described arrangement of the sealing rings 33, an axially short construction of the bearing ring 30 can be achieved with a plurality of axially adjacent annular channels 31. This is made possible by the fact that the sealing rings 33 according to the invention need not be accommodated in each case in an independent annular web. In two in the manner described above with sealing rings 33 formed, axially adjacent annular channels 31 may be located axially between these annular channels 31, a further annular channel 31, which in itself is not lined with sealing rings 33. Here, the adjacent sealing rings 33 take over the function of axial boundary walls for the sealing ring-free annular channel 31st
  • this bearing ring design in principle follows one with that of the ring channel design Fig. 5 matching alternative on.
  • the alternative consists exclusively in that for the position stabilization of the sealing rings 33 on the adjacent groove flanks of the annular channels 31st no anchors 34 secured in the bottom of these annular channels 31 are provided.
  • the position assurance takes place here rather by retaining means which are integrated in the sealing rings 33 themselves.
  • These holding means can be of various types and basically only serve to secure the sealing rings 33 in their position on the side flanks of the annular channels 31, without obstructing a fluid flow through the respective annular channels 31 excessively.
  • FIG. b The exploded view in Figure section b shows two sealing rings 33, which are combined to form a so-called tandem ring.
  • This summarization is given by the fact that two, each slotted on its circumference sealing rings 33 are connected at one of their butt ends via a bridge member 35, from which for Stoßspaltüberbrückung a web 36 with, for example, H-shaped cross-section in the axial gap of the second end the impact gap forming ends of the sealing rings 33 extends.
  • the bearing ring according to this embodiment has an outer circumference with a constant diameter. In this outer wall open the radial bores 32 of the bearing ring 30th
  • the annular channels 31 are formed in this embodiment of sealing rings 33, which are axially interposed between each a radial bore 32 in receiving grooves in the outer wall portion of the bearing ring 30 positively inserted. Since these sealing rings 33 are each mounted over substantially the entire circumference of the bearing ring 30 in continuous bearing ring material and adjacent only in the radial bores 32 directly or indirectly to this, an axially short design of the respective bearing ring 30 can be achieved here.
  • the bearing rings can be outwardly exciting, circumferentially slotted rings in the nature of piston rings and made of metal or plastic.
  • closed sealing rings made of elastically extensible material. These may have the cross-section of about an H.
  • the upstanding legs serve as sealing rings 33 of a sealing ring tandem and the central web as a spacer.
  • the middle bar must of course be provided with flow openings.
EP06705778A 2005-02-03 2006-01-13 Verstellbare nockenwelle, insbesondere für verbrennungsmotoren von kraftfahrzeugen, mit einer hydraulischen stelleinrichtung Expired - Fee Related EP1844216B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005005212 2005-02-03
DE102005040934A DE102005040934A1 (de) 2005-02-03 2005-08-30 Verstellbare Nockenwelle, insbesondere für Verbrennungsmotoren von Kraftfahrzeugen, mit einer hydraulischen Stelleinrichtung
PCT/DE2006/000039 WO2006081789A1 (de) 2005-02-03 2006-01-13 Verstellbare nockenwelle, insbesondere für verbrennungsmotoren von kraftfahrzeugen, mit einer hydraulischen stelleinrichtung

Publications (2)

Publication Number Publication Date
EP1844216A1 EP1844216A1 (de) 2007-10-17
EP1844216B1 true EP1844216B1 (de) 2009-10-28

Family

ID=36177570

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06705778A Expired - Fee Related EP1844216B1 (de) 2005-02-03 2006-01-13 Verstellbare nockenwelle, insbesondere für verbrennungsmotoren von kraftfahrzeugen, mit einer hydraulischen stelleinrichtung

Country Status (6)

Country Link
US (1) US7513232B2 (ja)
EP (1) EP1844216B1 (ja)
JP (1) JP4751402B2 (ja)
CN (1) CN1942657B (ja)
DE (2) DE102005040934A1 (ja)
WO (1) WO2006081789A1 (ja)

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DE102006013829A1 (de) * 2006-03-23 2007-09-27 Mahle International Gmbh Verstellbare Nockenwelle
DE102006024794A1 (de) 2006-05-27 2007-12-06 Mahle International Gmbh Verstellbare Nockenwelle
DE102006041918A1 (de) 2006-09-07 2008-03-27 Mahle International Gmbh Verstellbare Nockenwelle
GB2444943B (en) * 2006-12-19 2011-07-13 Mechadyne Plc Camshaft and phaser assembly
DE102007024092A1 (de) * 2007-05-22 2008-11-27 Mahle International Gmbh Nockenwelle
EP2171222B1 (en) * 2007-07-02 2017-11-29 BorgWarner Inc. Concentric cam with check valves in the spool for a phaser
JP5034869B2 (ja) * 2007-10-29 2012-09-26 トヨタ自動車株式会社 可変バルブタイミング装置
DE102008033230B4 (de) 2008-01-04 2010-05-27 Hydraulik-Ring Gmbh Doppelter Nockenwellenversteller in Schichtaufbau
US7841311B2 (en) 2008-01-04 2010-11-30 Hilite International Inc. Variable valve timing device
GB2467943A (en) * 2009-02-23 2010-08-25 Mechadyne Plc I.c. engine double overhead camshaft phasing system
DE102010033296A1 (de) 2010-08-04 2012-02-09 Hydraulik-Ring Gmbh Nockenwellenversteller, insbesondere mit Nockenwelle
US8695545B2 (en) 2011-03-31 2014-04-15 Toyota Jidosha Kabushiki Kaisha Phase changing device of camshaft
DE102011076652B4 (de) 2011-05-27 2017-06-01 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der relativen Drehwinkelposition geschachtelter Nockenwellen
DE102011077563B4 (de) * 2011-06-15 2022-08-11 Mahle International Gmbh Brennkraftmaschine
DE102011051480B4 (de) 2011-06-30 2014-11-20 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit axial verschiebbarem Nockenpaket
DE102011054350A1 (de) * 2011-10-10 2013-04-11 Thyssenkrupp Presta Teccenter Ag Nockenwelle sowie Funktionselemente für eine Nockenwelle
US9140151B2 (en) * 2011-12-27 2015-09-22 Honda Motor Co., Ltd. Valve gear
DE102012203145A1 (de) * 2012-02-29 2013-08-29 Mahle International Gmbh Verstellbare Nockenwelle
DE102012206500A1 (de) * 2012-04-19 2013-10-24 Mahle International Gmbh Brennkraftmaschine
DE102012103581A1 (de) * 2012-04-24 2013-10-24 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit durch Drucköl beölbare, verstellbare Nocken
DE102012220652A1 (de) * 2012-11-13 2014-05-15 Mahle International Gmbh Nockenwelle
US9920661B2 (en) * 2013-05-16 2018-03-20 Schaeffler Technologies AG & Co. KG Camshaft phaser with a rotor nose oil feed adapter
DE102013106747A1 (de) * 2013-06-27 2014-12-31 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
DE102013106746A1 (de) * 2013-06-27 2014-12-31 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
DE102014109103A1 (de) * 2014-06-30 2015-12-31 Thyssenkrupp Presta Teccenter Ag Nockenwelle für den Ventiltrieb einer Brennkraftmaschine mit variierbarer Ventilöffnungsdauer
DE102015215292A1 (de) * 2015-08-11 2017-02-16 Thyssenkrupp Ag Verfahren und Vorrichtung zur Montage einer verstellbaren Nockenwelle
US10352200B2 (en) 2015-09-30 2019-07-16 Honda Motor Co., Ltd. Cam shaft
JP6396936B2 (ja) * 2016-03-18 2018-09-26 本田技研工業株式会社 カムシャフトの製造方法
CN113048218A (zh) * 2021-03-09 2021-06-29 燕山大学 一种适用于柔性传动链的防爆动滑轮

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Also Published As

Publication number Publication date
WO2006081789A1 (de) 2006-08-10
JP2008528871A (ja) 2008-07-31
DE102005040934A1 (de) 2006-08-17
DE502006005236D1 (de) 2009-12-10
US7513232B2 (en) 2009-04-07
JP4751402B2 (ja) 2011-08-17
CN1942657A (zh) 2007-04-04
CN1942657B (zh) 2010-06-16
EP1844216A1 (de) 2007-10-17
US20070240657A1 (en) 2007-10-18

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