EP1336031B1 - Vorrichtung zur relativen drehwinkelverstellung einer nockenwelle einer brennkraftmaschine zu einem antriebsrad - Google Patents

Vorrichtung zur relativen drehwinkelverstellung einer nockenwelle einer brennkraftmaschine zu einem antriebsrad Download PDF

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Publication number
EP1336031B1
EP1336031B1 EP01984686A EP01984686A EP1336031B1 EP 1336031 B1 EP1336031 B1 EP 1336031B1 EP 01984686 A EP01984686 A EP 01984686A EP 01984686 A EP01984686 A EP 01984686A EP 1336031 B1 EP1336031 B1 EP 1336031B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
inner part
bore
locking member
pressure
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 - Lifetime
Application number
EP01984686A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1336031A1 (de
Inventor
Edwin Palesch
Martin Maier
Gordon Rein
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.)
Dr Ing HCF Porsche AG
Hilite Germany GmbH
Original Assignee
Dr Ing HCF Porsche AG
Hydraulik Ring 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 Dr Ing HCF Porsche AG, Hydraulik Ring GmbH filed Critical Dr Ing HCF Porsche AG
Publication of EP1336031A1 publication Critical patent/EP1336031A1/de
Application granted granted Critical
Publication of EP1336031B1 publication Critical patent/EP1336031B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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

Definitions

  • the invention relates to a device for the relative rotation angle adjustment Camshaft of an internal combustion engine to a drive wheel according to the genus of Main claim.
  • the in DE 196 23 818 A1 Device shown is designed so that the pressurization to the Hydraulic chambers, through which the adjustment of the rotor relative to the stator of the Camshaft adjuster and the hydraulic pressurization to Unlocking the locking pin is done in parallel.
  • this is not always safe that the adjustment unit is unlocked before the rotor via the pressure or hydraulic chambers formed in the adjustment unit into a Adjustment position is transferred. This can result in operating states in which the Adjustment unit does not work reliably.
  • Camshaft adjuster is advantageously by a first adjustment stroke Locking element first transferred to an unlocking position, but in the both the hydraulic channel controlled by the locking element and that to the other oil supply holes leading to pressure chambers are still closed. Becomes however, the locking element is raised beyond its unlocked position, so the hydraulic channel leading to the pressure chamber of the adjustment unit is released before after a short initial adjustment travel of the rotor of the adjustment unit, also those to oil supply holes leading to the remaining pressure chambers are released and so that the rotor continues in the desired manner relative to the stator of the adjusting unit can be adjusted.
  • This type of pressurization causes a rattling start of the camshaft adjuster prevented or reduced; the soffit can continue of the locking element can be reduced in the locking hole. So that will the lifespan and functionality of the locking device have been significantly improved.
  • the locking element is received in a hole that is in a web or Wing of the rotor is arranged.
  • the hole is in a hydraulic oil supply line arranged, which leads to a pressure chamber arranged in the adjusting unit. is the locking element is in a locked position, the hydraulic line closed by the locking element; in an unlocked position that gives Locking element free the hydraulic line to the pressure chamber.
  • the camshaft of an internal combustion engine is schematic with 2 indicated, at the free end of the rotor, hereinafter referred to as inner part 4, an adjusting unit 6 is arranged in a rotationally fixed manner.
  • the inner part 4 is in the present Embodiment provided with three radially arranged webs 8a to 8c, the from a hub 10 of the inner part 4 go out.
  • the inner part 4 is in the area of its webs 8a to 8c by a cellular wheel 12, which has three inwardly projecting radial Web 14 a to 14 c is provided.
  • Cell wheel 12 is on its end facing the camshaft 12 by a Sprocket 16 completed that rotatable and sealing on the hub 10 of the Inner part 4 is guided.
  • the sprocket 16 serves to drive the camshaft for example via a control or drive chain connected to the crankshaft he follows.
  • the opposite end face of the cellular wheel 12 is supported by a disk 18 closed, the sprocket 16, the disc 18 and the cellular wheel 12 not over Screw means shown are firmly connected.
  • the hub 10 has a central bore 28, which in the camshaft 2 is continued and one with a smaller one Connected diameter bore 30 in which the screw 26th is attached.
  • the pressure spaces 24a to 24c are three in the hub 10 of the inner part 4th arranged and radially running bores 32a to 32c with an annular space 34 connected, which is between the fastening screw 26 for the adjusting unit 6 and the wall section provided in the hub 10 and in the camshaft 2 central bore 28 forms, the annular space 34 through the head 36 of the screw 26 is closed at the end.
  • the annular space 34 is provided with a plurality of bores 38 running radially in the camshaft 2 connected to an annular groove 40 arranged on the outer circumference of the camshaft 2.
  • Three further bores arranged on the outer circumference of the hub 10 and running radially 42a to 42c are on the one hand depending on the rotational position of the inner part 4 opposite the cellular wheel 12 (explained in more detail later) with one of the three Pressure spaces 22a to 22c connected; on the other hand, they are with a Outer periphery of the camshaft 2 arranged annular groove 44 connected axially over five in the camshaft 2 bores 46a to 46e to another, also on Guide the outer circumference of the camshaft 2 formed annular groove 48.
  • the two ring grooves 40 and 44 are each via a acting as a rotary union Camshaft bearing 50 connected to two control lines 52 and 54 leading to one Control valve 56 designed as a 4/2 proportional control valve.
  • the Control line 52 is connected to the output A of the control valve 56, while the Control line 54 leads to the output B of the control valve 56. That has on the input side Control valve 56 via a pressure port P, which has a check valve 58 and a Pressure medium pump 60 is connected to an oil tank 62 and via a connection T, which also leads to the oil tank 62.
  • a bore 64 in the web 8a provided in which a locking element, hereinafter referred to as locking bolt 66 designated, is arranged
  • the bore 64 is formed as a stepped bore, in which larger bore section 64a the head portion of the ring shoulder 66a Locking bolt 66 is guided, while in the smaller bore section 64b Stepped bore 64 of the actual locking bolt 66 is guided.
  • the Locking bolt 66 has an opening 68 in which a compression spring 70 is arranged between the bottom of the opening 68 and one on the disk 18 supporting plastic disc 72 arranged in the bore section 64a is clamped.
  • the plastic disc 72 has a central opening 74 which over a channel, not shown, is connected to the oil tank 62 Moving the locking bolt 66 against the spring force of the compression spring 70 in leakage oil from the opening 68 escape.
  • a stepped bore 76 is made in the sprocket 16, in a first Bore section 76a of the locking bolts 66 for locking the inner part 4th engages with the sprocket 16 or the cellular wheel 12.
  • a second bore portion 76b which is smaller in diameter is formed as the diameter of the locking bolt 66.
  • a crescent-shaped groove 78 is arranged, which extends into the stepped bore 76 extends into and communicates with the second bore portion 76b.
  • a radial through bore 80 is arranged in the web 8a, on the one hand, with the axial bore 46a and communicates with the annular groove 44 and on the other Leads to groove 78.
  • the web 8a there is also a connection channel Bore 82 provided, that of the larger bore portion 64a in the radial direction leads to the pressure chamber 22a
  • the adjusting unit 6 with its in FIGS. 1 to 3 provided end position for the adjustment of an intake camshaft, wherein the cellular wheel 12 is driven clockwise and the inner part 4 in Clockwise in the direction of "early" opening of the intake valves can be adjusted.
  • the internal combustion engine is in the position shown in FIG. 1 Operation, i.e. at standstill.
  • the locking bolt 66 is in its locked Position, i.e. it is through the compression spring 70 in the bore portion 76a of the sprocket 16 locked So that the inner part 4 is opposite the cellular wheel 12 in one End position which corresponds to a "late" opening or closing time of the cam and Cam follower actuated intake valves of the internal combustion engine corresponds.
  • the Control valve 56 is de-energized, so that via the output A of the control valve 56, the Control line 52, the annular groove 40, the radial bores 38, the annular space 34 and the radial bores 32a to 32c the pressure oil supply to the pressure chambers 24a to 24c is released for the starting process of the internal combustion engine.
  • the control valve 56 is energized and thus the pressure oil supply to the Output B switched (see Fig. 2).
  • the pressure oil supply now runs over the Control line 54, the annular groove 48, the axial bores 46a to 46e to the annular groove 44. From the annular groove 44 on the one hand the three radial bores 42a to 42c and on the other hand, the bore 80 leading to the locking bolt 66 with pressure oil fed.
  • the pressure oil supply via the radial bores 42a to 42c to the three Pressure chambers 22a to 22c is still blocked because in the end position of the Camshaft phaser the radial bores 42a to 42c from the radial webs 14a to 14c of the cellular wheel 12 are covered or sealed (see FIG. 2c).
  • the oil passage leading to the locking bolt 66 (bore 80) is open, so that he through the one below his ring shoulder 66a and the one on his face 66b oil pressure developing from the bore section arranged in the chain wheel 16 76a is lifted out and thus the adjusting unit 6 is unlocked.
  • the Pressure oil supply to the end face 66b of the locking bolt 66 takes place via the groove 78 leading to bore section 76b.
  • the hydraulic oil thus passes through the bore 80 into the pressure chamber 22a.
  • the system is designed so that at an adjustment speed of the internal combustion engine Hydraulic oil supplied to the pressure chamber 22a, the inner part 4 by the angle ⁇ clockwise adjusted (see Fig. 4b).
  • This initial adjustment path means that the inner part 4 arranged radial bores 42a to 42c from their complete overlap the radial webs 14a to 14c of the cellular wheel 12 out, so that Hydraulic oil via the radial bores 42a to 42c into the pressure chambers 22a to 22c arrives.
  • the inner part 4 can thus face the adjusting unit 6 the cellular wheel 12 up to a maximum adjustment angle ⁇ 'in the direction of "early" opening of the inlet valves can be adjusted.
  • camshaft adjuster in which the locking bolt of the Camshaft adjuster itself a valve function for the supply of hydraulic oil to the Exercises pressure rooms is not limited to the described embodiment. It can also be used with camshaft adjusters that generally have one Have locking mechanism and which a clear time sequence of Unlock and adjust should be assigned.
  • camshaft adjusters that generally have one Have locking mechanism and which a clear time sequence of Unlock and adjust should be assigned.
  • These include, for example So-called axial camshaft adjuster, in which one in the housing part (stator) of the Camshaft adjuster arranged hydraulic piston is guided longitudinally and via a helical toothing with the part connected to the camshaft in a rotationally fixed manner (Rotor) of the camshaft adjuster works together. Due to the helical teeth the axial displacement of the piston in an angle of rotation adjustment of the camshaft implemented.
  • a locking unit locking the piston can operate simultaneously the previously described valve function for the supply of hydraulic oil to the pressure chamber of the Take over the camshaft adjuster.
  • the control for unlocking and adjusting is can of course also be used for camshaft adjusters that are based on exhaust camshafts from Internal combustion engines are arranged.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP01984686A 2000-11-08 2001-10-24 Vorrichtung zur relativen drehwinkelverstellung einer nockenwelle einer brennkraftmaschine zu einem antriebsrad Expired - Lifetime EP1336031B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10055334 2000-11-08
DE10055334A DE10055334C2 (de) 2000-11-08 2000-11-08 Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad
PCT/EP2001/012262 WO2002042613A1 (de) 2000-11-08 2001-10-24 Vorrichtung zur relativen drehwinkelverstellung einer nockenwelle einer brennkraftmaschine zu einem antriebsrad

Publications (2)

Publication Number Publication Date
EP1336031A1 EP1336031A1 (de) 2003-08-20
EP1336031B1 true EP1336031B1 (de) 2004-04-21

Family

ID=7662561

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01984686A Expired - Lifetime EP1336031B1 (de) 2000-11-08 2001-10-24 Vorrichtung zur relativen drehwinkelverstellung einer nockenwelle einer brennkraftmaschine zu einem antriebsrad

Country Status (5)

Country Link
US (1) US6742486B2 (ja)
EP (1) EP1336031B1 (ja)
JP (1) JP4113430B2 (ja)
DE (2) DE10055334C2 (ja)
WO (1) WO2002042613A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012652A1 (de) 2010-03-25 2011-09-29 Hydraulik-Ring Gmbh Schwenkmotornockenwellenversteller mit einem Rotor

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4859451A (en) * 1984-10-04 1989-08-22 Salutar, Inc. Paramagnetic contrast agents for MR imaging
DE10246838A1 (de) 2002-10-08 2004-04-29 Daimlerchrysler Ag Verriegelungseinrichtung für einen Nockenwellenversteller
US6772721B1 (en) * 2003-06-11 2004-08-10 Borgwarner Inc. Torsional assist cam phaser for cam in block engines
GB0505497D0 (en) * 2005-03-18 2005-04-20 Mechadyne Plc Camshaft to phaser coupling
DE102005020529A1 (de) 2005-05-03 2006-11-09 Schaeffler Kg Nockenwellenversteller
US7325773B2 (en) * 2005-06-30 2008-02-05 Gregory J. Gorrie Kite winch and method for pulling-in a kite
US7240651B1 (en) * 2006-03-30 2007-07-10 Ford Global Technologies, Llc Variable cam timing damper
FR2906835B1 (fr) * 2006-10-06 2008-12-19 Renault Sas Procede et dispositif commandant un systeme de decalage angulaire et vehicule muni du dispositif
US20100092925A1 (en) * 2008-10-15 2010-04-15 Matvey Lvovskiy Training simulator for sharp shooting
JP6255777B2 (ja) * 2013-07-31 2018-01-10 アイシン精機株式会社 弁開閉時期制御装置
CN109281724B (zh) * 2017-07-21 2022-07-26 舍弗勒技术股份两合公司 凸轮轴调节器和内燃机

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0192504A (ja) * 1987-09-30 1989-04-11 Aisin Seiki Co Ltd 弁開閉時期制御装置
US5823152A (en) * 1995-06-14 1998-10-20 Nippondenso Co., Ltd. Control apparatus for varying a rotational or angular phase between two rotational shafts, preferably applicable to a valve timing control apparatus for an internal combustion engine
JP3116858B2 (ja) * 1996-11-29 2000-12-11 トヨタ自動車株式会社 内燃機関のバルブタイミング可変機構
US5836277A (en) * 1996-12-24 1998-11-17 Aisin Seiki Kabushiki Kaisha Valve timing control device
JP3760568B2 (ja) * 1997-06-05 2006-03-29 アイシン精機株式会社 弁開閉時期制御装置
JPH1150820A (ja) * 1997-08-05 1999-02-23 Toyota Motor Corp 内燃機関のバルブタイミング制御装置
JP4147435B2 (ja) * 1998-01-30 2008-09-10 アイシン精機株式会社 弁開閉時期制御装置
JP4203703B2 (ja) * 2000-06-14 2009-01-07 アイシン精機株式会社 弁開閉時期制御装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012652A1 (de) 2010-03-25 2011-09-29 Hydraulik-Ring Gmbh Schwenkmotornockenwellenversteller mit einem Rotor
DE102010012652B4 (de) 2010-03-25 2018-05-17 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einem Rotor

Also Published As

Publication number Publication date
DE10055334C2 (de) 2003-10-30
JP4113430B2 (ja) 2008-07-09
JP2004514818A (ja) 2004-05-20
WO2002042613A1 (de) 2002-05-30
US6742486B2 (en) 2004-06-01
EP1336031A1 (de) 2003-08-20
DE10055334A1 (de) 2002-05-23
US20030154944A1 (en) 2003-08-21
DE50102082D1 (de) 2004-05-27

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