EP1544420B1 - Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle - Google Patents

Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle Download PDF

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Publication number
EP1544420B1
EP1544420B1 EP04026407A EP04026407A EP1544420B1 EP 1544420 B1 EP1544420 B1 EP 1544420B1 EP 04026407 A EP04026407 A EP 04026407A EP 04026407 A EP04026407 A EP 04026407A EP 1544420 B1 EP1544420 B1 EP 1544420B1
Authority
EP
European Patent Office
Prior art keywords
stator
walls
web walls
web
rotor
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
EP04026407A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1544420A2 (de
EP1544420A3 (de
Inventor
Ulrich Wierl
Mike Kohrs
Rainer Ottersbach
Jochen Auchter
Hermann Wiehl
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
Publication of EP1544420A2 publication Critical patent/EP1544420A2/de
Publication of EP1544420A3 publication Critical patent/EP1544420A3/de
Application granted granted Critical
Publication of EP1544420B1 publication Critical patent/EP1544420B1/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
    • 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
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • F01L1/344—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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

Definitions

  • the invention relates to an internal combustion engine having a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft, comprising: a rotor with vanes disposed thereon, which is non-rotatably connected to the camshaft, a frontally provided with an end wall stator, the rotationally fixed with a driven by the crankshaft Drive wheel is connected, wherein on both sides of the wing pressure chambers are provided which are each bounded by web walls and inner and outer, in the circumferential direction, concentrically extending walls of the stator and are pressurizable or emptied via a hydraulic system with hydraulic fluid.
  • From the DE 101 34 320 A1 is an internal combustion engine with a generic Hydraulic device for adjusting the rotational angle of a camshaft known that can change the phase angle of a camshaft relative to a crankshaft.
  • This device consists of a rotor and a stator, of which the former, designed as an impeller, comprises the camshaft and rotates synchronously with it.
  • the stator is on the one hand closed by a front wall, which may be part of a housing surrounding the stator, and on the other hand by a drive wheel pressure-sealed. It includes the rotor and rotates synchronously with the driven by the crankshaft drive wheel.
  • Essentially radially extending web walls in the stator allow only a limited angle of rotation of the rotor and form with this a plurality of pressure chambers, which can be pressurized with hydraulic fluid or emptied.
  • a proposal for reducing the weight of the device for adjusting the rotational angle for example, the DE 101 48 687 A1 or the DE 101 34 320 A1 can be removed by parts of the device made of aluminum or an aluminum alloy or another light metal.
  • This has the disadvantage that due to different coefficients of thermal expansion, the leakage gaps can increase over the heating and thus results in a high leakage.
  • aluminum deforms more under load than steel or iron.
  • housing screws together correspondingly large gaps must allow deformation.
  • the housing screws represent an increased construction cost, thus causing higher costs and also have a non-optimal power flow for the device result.
  • the invention is therefore based on the object to design a device for adjusting the rotational angle of a camshaft relative to a crankshaft for an internal combustion engine such that on the one hand, a reduction in mass of the device takes place on the other hand while minimizing the leakage.
  • the DE 199 51 390 A1 discloses a device for hydraulic rotation angle adjustment of a shaft relative to a drive wheel, wherein a wave side arranged plate cooperates with the drive wheel or a drive wheel side arranged component for adjusting the rotational angle.
  • the device has at least one ring-shaped formation in the plate and provided on the drive wheel or the component means which cooperate with the formation in such a way that it is subdivided into two separate chambers.
  • the device is provided with means for selective hydraulic loading of the chambers for adjusting the relative rotational position of the drive wheel and shaft.
  • the object is achieved in a device for an internal combustion engine with the features of the preamble of claim 1, characterized in that essential parts of the stator, in particular its web walls and its inner and outer walls, and optionally the housing with a possibly disposed therein sealing disc produced as chipless Sheet metal parts are formed.
  • essential parts of the stator in particular its web walls and its inner and outer walls, and optionally the housing with a possibly disposed therein sealing disc produced as chipless Sheet metal parts are formed.
  • sheet instead of sheet also band can be used, being used in the following sheet as a generic term for sheet or strip.
  • the solid sintered components as pressure chamber forming units of the drive side are thus replaced by thin-walled sheet metal and Blechumformmaschine.
  • these sheets can be ideally adapted to the load locally along the load directions by means of formations or corresponding profilings, without the need for globally larger wall thicknesses and thus a high mass being taken into account .
  • this has the advantage that the thermal expansion coefficient of all components remains the same and thus no leaks due to thermal effects can arise.
  • the stator consists of inner and outer circumferential walls and web walls.
  • the web walls each connect two ends of adjacent inner and outer circumferentially extending walls and extend substantially radially.
  • the web walls are not exactly radial, but have a certain angle to the radial or they are not flat, but recesses, for example, to prevent jamming of the wings in their end positions.
  • the stator is made of thin-walled sheet metal, it is not as dimensionally stable as a sintered stator known in the art. It is possible to attach the stator directly to the torque-transmitting component via integral connection possibilities. In order to achieve a comparable bending and compression stiffness as that of the sintered stator, but it can be used in a comprehensive housing him ( FIG. 2a ), with the joining technologies of the forming technology or by general force, form, friction-locking technologies such as knurling, flanging, welding, caulking, riveting, gluing or bent retaining lugs is connected to the drive wheel. The housing then takes over the connection of the stator to the drive wheel as torque-transmitting and radial load-transferable component and the seal. It also prevents vibrations from occurring on the stator due to introduced radial forces.
  • the housing seals the stator on one end face and forms an end wall there. If the stator walls do not form a right angle to the end wall, the sealing of the pressure chambers is not completely guaranteed. To avoid leakage losses, it is therefore advantageous to arrange a sealing disc immediately in front of the end wall, so that after connecting the end wall with the stator and inserting the rotor with wings perpendicular pressure chambers arise.
  • the stability of the housing can be additionally increased by connecting the sealing disc firmly to the end wall.
  • the sealing disc is preferably profiled from thin-walled sheet metal and adapted to the size and shape of the stator.
  • non-cutting parts made of metal strips. If necessary, as in the case of the stator, the strip must be formed into a ring at one point and then firmly connected, for example by welding.
  • the non-cutting production of the stator and the housing of course does not mean that these parts are not machined, if very high accuracy should be required.
  • a second way to increase the bending and compressive rigidity of the stator is to form the web walls so that they can transmit radial forces and / or circumferential forces ( FIG. 3a ).
  • the support of the radial chain or belt force can internally between stator and rotor or externally between Camshaft or an extension of the rotor and sprocket or made a combination of both possibilities. It has proved particularly advantageous not to form the web walls exactly radially, but make in a range of 10 ° to 30 ° to the radial, so that the wings touch the radially outer web wall ends in their end positions.
  • a third embodiment is a tubular stator, the web walls are formed as retracted webs.
  • the remaining, closed ring surface saves the housing. This further reduces the mass.
  • the sealing washer can be inserted and then sealed the edge and firmly connected.
  • the annular surface absorbs the radial forces and prevents the stator from vibrating.
  • the radially extending walls may also be formed as open ends, then being used for storage and sealing in the rotor sliding shoes.
  • the sliding blocks are designed and arranged such that they support the web walls formed as retracted webs against each other. This prevents bending of the web walls.
  • the wall thickness of the radially extending walls of the stator can be further reduced by preventing the vanes of the rotor from abutting and exerting pressure in their respective end positions against the radially extending walls of the stator.
  • a Verstellwinkelbegrenzung is necessary. This can, for example, via an associated with the rotor element Verstellwinkelbegrenzung that in a corresponding backdrop engages, be realized.
  • the inventively designed device is thus easier compared to a device of the prior art, requires less cutting work and thus reduces the manufacturing costs and can also do without a resin impregnation or steam treatment of sealing the now no longer required sintered material.
  • a hydraulic device 1 for the rotational angle adjustment of a camshaft 2 with respect to a crankshaft, not shown, which is designed as a hydraulic actuator.
  • This device 1 is driven by a drive wheel 3, which is connected for example by a chain, not shown, with the crankshaft.
  • the device 1 consists of a fixedly connected to the drive wheel 3 stator 4, which is closed by a front wall 5 and the drive wheel 3 fluid-tight, and a rotatably connected by an axial central screw 21 with the camshaft 2 rotor 6, wherein the rotor is designed as an impeller.
  • the stator 4 of the device 1 forms by web walls 7, 7 ', 7 “and by outer 8, 8', 8” and inner 9, 9 ', 9 “, extending in the circumferential direction walls with the rotor 6 and its wings 10 first pressure chambers 11, 11 ', 11 "and second pressure chambers 12, 12', 12", which, filled with hydraulic fluid, produce an angular displacement between rotor 6 and stator 4.
  • the rotor 6 and the stator 4 are arranged in a housing 13 which surrounds the The first 11, 11 ', 11 "and second 12, 12', 12" pressure chambers are sealed to the outside by means of an element 16, which adjoins the rotor 6 for adjustment angle limiting, which engages in a corresponding link 17, limiting the adjustment range of the Rotor 6, which reduces the burden of the stator 4.
  • a sealing washer 14 is inserted, which is adapted to the diameter of the stator 4.
  • FIG. 2 are the web walls 7, 7 ', 7 "not exactly formed radially, but at an angle of about 20 °, so that the wings 10 in their end positions, the radially outer ends of the web walls 7, 7', 7" touch.
  • the bending and compressive rigidity of the stator 4 is increased, and it is possible to transmit radial forces and circumferential forces
  • FIG. 3 shows a cross section of a second version of a tubular stator 4. It forms by its substantially radially extending web walls 7, 7 ', 7 "and its inner 8, 8', 8" and outer 9, 9 ', 9 “, in Circumferentially extending walls with the rotor 6, not shown in this figure, the first 11, 11 ', 11 "and second 12, 12', 12" pressure chambers ..
  • the stator 4 itself is arranged in a cylindrical housing 13 such that the housing 13 and the outer, circumferentially extending walls 9, 9 ', 9 "touch each other, whereby the rigidity of the stator 4 is increased and vibrations due to radial forces are damped.
  • the rigidity can be further increased by filling the hollow chambers or incisions 15, 15 ', 15 "formed by the housings 13 and stator 4, for example, with metal foam, so that the wings 10 do not jam in the end positions, it is advantageous to radially extending web walls in two parts, such that they have at least a first, radially extending part 20, to which the wings abut and at least one further part.
  • FIGS. 4a and 4b show a cross-section and a perspective view of a third embodiment of a stator 4.
  • this third stator 4 is stiffer with respect to a radial force absorption. It is particularly advantageous to set the web walls such that the respective adjacent web walls 7, 7 'and the housing 13 prevent spreading under radial force (self-locking).
  • FIGS. 5a and 5b show a cross section and a perspective view
  • a particularly advantageous feature of this design is that the housing 13, with the exception of the end wall 5, can be saved by the remaining, closed annular surface, the circular outer wall 18.
  • the sealing disc 14 (FIG. FIG. 1 ), which is used on the front side of the stator 4 and whose edge can be crimped, for example. From the circular outer wall 18 arise by punching, for example, the web walls 7, 7 'which are then bent inwards.
  • the web walls 7, 7 ', 7 "are well deformable by their open ends FIG. 6b may be formed and then sealed with sliding shoes 19.
  • FIG. 6a and 6b show a perspective view of a part of a fifth and sixth stator 4, the variants of the fifth stator 4 represent.
  • These stator variants 4 are therefore inserted into a housing 13.
  • a similar rigidity as in the devices of the prior art is achieved by the illustrated embodiments of the stator 4.
  • the leakage losses are reduced, as can be dispensed with porous sintered components or a complex steam treatment or resin impregnation.

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)
  • Gasket Seals (AREA)
EP04026407A 2003-12-16 2004-11-06 Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle Not-in-force EP1544420B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10358888 2003-12-16
DE10358888.4A DE10358888B4 (de) 2003-12-16 2003-12-16 Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle

Publications (3)

Publication Number Publication Date
EP1544420A2 EP1544420A2 (de) 2005-06-22
EP1544420A3 EP1544420A3 (de) 2008-08-27
EP1544420B1 true EP1544420B1 (de) 2010-07-28

Family

ID=34485404

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04026407A Not-in-force EP1544420B1 (de) 2003-12-16 2004-11-06 Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle

Country Status (9)

Country Link
US (1) US7284516B2 (pt)
EP (1) EP1544420B1 (pt)
JP (1) JP4608300B2 (pt)
KR (1) KR101119457B1 (pt)
CN (1) CN100439663C (pt)
AT (1) ATE475783T1 (pt)
BR (1) BRPI0406256B1 (pt)
DE (2) DE10358888B4 (pt)
RU (1) RU2353782C2 (pt)

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DE102005024242B4 (de) * 2005-05-23 2017-08-24 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102005024241B4 (de) 2005-05-23 2017-08-17 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
GB2431977A (en) * 2005-11-02 2007-05-09 Mechadyne Plc Camshaft assembly
DE102006036052B4 (de) * 2006-08-02 2018-03-08 Schaeffler Technologies AG & Co. KG Dichtblech für einen Nockenwellenversteller und Nockenwellenversteller mit einem Dichtblech
DE102007039282B4 (de) 2007-08-20 2017-06-01 Hilite Germany Gmbh Hydraulisch dichter Nockenwellenversteller
DE102007056550A1 (de) * 2007-11-23 2009-05-28 Schaeffler Kg Modular aufgebauter Nockenwellenversteller mit Ketten- oder Riemenrad
DE102008032031A1 (de) 2008-07-07 2010-01-14 Schaeffler Kg Nockenwellenversteller
DE102009041768B4 (de) * 2008-10-09 2020-10-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller für eine konzentrische Nockenwelle
JP4900451B2 (ja) * 2009-11-09 2012-03-21 株式会社デンソー バルブタイミング調整装置
DE102010022897A1 (de) * 2010-06-07 2011-12-08 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine sowie Schraube für eine solche Vorrichtung
DE102010024596A1 (de) * 2010-06-22 2011-12-22 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zum Steuern und/oder zum Beeinflussen der Ventilsteuerzeiten einer Brennkraftmaschine
JP5177715B2 (ja) * 2010-12-02 2013-04-10 株式会社デンソー バルブタイミング調整装置およびその組立方法
DE102010063706A1 (de) * 2010-12-21 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller mit Rückstellfeder
JP5569458B2 (ja) * 2011-04-18 2014-08-13 株式会社デンソー バルブタイミング調整装置
JP5929300B2 (ja) * 2011-08-08 2016-06-01 日産自動車株式会社 エンジンのバルブタイミング制御装置
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DE102012205705B4 (de) * 2012-04-05 2018-02-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit einem An- und/oder Abtriebselement in Sandwichbauweise sowie ein Verfahren zur Herstellung des An- bzw. Abtriebselement in Sandwichbauweise
DE102012218405B4 (de) * 2012-10-10 2014-08-21 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller mit rollierter Verbindung
CN102926831A (zh) * 2012-10-30 2013-02-13 芜湖杰锋汽车动力系统有限公司 一种配气调节装置
DE102013204929A1 (de) * 2013-03-20 2014-09-25 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102014200818A1 (de) * 2014-01-17 2015-01-08 Schaeffler Technologies Gmbh & Co. Kg Zweigeteilter Stator mit kaltverschweißtem Deckel
CN103953408B (zh) * 2014-04-30 2016-08-17 桂林电子科技大学 无极可变配气定时机构
DE102016220829A1 (de) 2016-10-24 2018-04-26 Schaeffler Technologies AG & Co. KG Stator mit hintereinander angeordneten Druckkammer-Segmenten und Nockenwellenversteller
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Also Published As

Publication number Publication date
CN100439663C (zh) 2008-12-03
KR20050061354A (ko) 2005-06-22
DE10358888A1 (de) 2005-07-21
KR101119457B1 (ko) 2012-03-15
ATE475783T1 (de) 2010-08-15
CN1629453A (zh) 2005-06-22
US20050155567A1 (en) 2005-07-21
BRPI0406256A (pt) 2005-09-06
EP1544420A2 (de) 2005-06-22
BRPI0406256B1 (pt) 2017-04-04
RU2004136796A (ru) 2006-05-27
EP1544420A3 (de) 2008-08-27
JP2005180434A (ja) 2005-07-07
US7284516B2 (en) 2007-10-23
RU2353782C2 (ru) 2009-04-27
DE10358888B4 (de) 2018-12-27
DE502004011438D1 (de) 2010-09-09
JP4608300B2 (ja) 2011-01-12

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