EP1589196A2 - Dispositif hydraulique pour la variation continue du calage d'arbre à cames - Google Patents

Dispositif hydraulique pour la variation continue du calage d'arbre à cames Download PDF

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Publication number
EP1589196A2
EP1589196A2 EP05007186A EP05007186A EP1589196A2 EP 1589196 A2 EP1589196 A2 EP 1589196A2 EP 05007186 A EP05007186 A EP 05007186A EP 05007186 A EP05007186 A EP 05007186A EP 1589196 A2 EP1589196 A2 EP 1589196A2
Authority
EP
European Patent Office
Prior art keywords
pendulum
pressure chamber
rotor
outer rotor
main 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.)
Ceased
Application number
EP05007186A
Other languages
German (de)
English (en)
Other versions
EP1589196A3 (fr
Inventor
Piet Pater
Holger Conrad
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP1589196A2 publication Critical patent/EP1589196A2/fr
Publication of EP1589196A3 publication Critical patent/EP1589196A3/fr
Ceased legal-status Critical Current

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    • 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 hydraulic device for continuously variable Adjustment of the camshaft of an internal combustion engine with one of a Crankshaft driven outer rotor and one of the camshaft assigned to this relatively rotatable inner rotor, wherein between Inner and outer rotor in the inner rotor on the one hand and in the outer rotor on the other hand pivotally mounted pendulum are arranged, which with between the pendulums lying rotor wings druckbeaufschlagbare Include main pressure chambers and in the rotary end positions to the Rotor blades abut.
  • Such devices allow an adjustment of the camshaft relative to the crankshaft and thus the timing of the cam this wave actuated valves and come inlet and / or outlet side for use. Benefits arise in particular with regard to emissions, Fuel consumption, torque curve and power development.
  • DE 199 61 567 A1 describes an initially mentioned Device for continuously variable camshaft adjustment, wherein the between inner and outer rotor arranged pendulum straight flanks have and in the Drehendlagen flat on the also straight sides rest against the wing of the inner rotor.
  • the flanks of the form Pendulum with the corresponding sides of the wings of the inner rotor wedge-shaped squeezing chambers, from which the oil from the inside to must be displaced externally; There are oil guides provided by the the oil can drain.
  • the object of the invention is, while avoiding the disadvantages mentioned dampened application of the pendulum to the corresponding wing sides in to allow the rotary end positions.
  • this is the contact surface between pendulum and rotor blades designed such that when investing a pendulum a rotor wing from the main pressure chamber a throttled drain exhibiting secondary pressure chamber is separable.
  • a pendulum for pivotal mounting in Inner rotor a cylindrical pendulum head and for pivoting and radial sliding bearing in the outer rotor a cylindrical, frontally flattened pendulum foot on.
  • a particularly preferred embodiment of the invention has a Pendulum between pendulum head and pendulum foot with pendulum head and Pendulum foot connected by webs, cylindrical-drop-shaped Pendulum on.
  • the transition from pendulum to the pendulum side The bridge has small radii forming a throttle edge at installation and the Transition from pendulum body to pendulum-head-side bar on large radii.
  • a rotor blade with the contour of a Pendulum has corresponding contact surface, wherein in the Rotary end positions in the area of the pendulum footbridge from the main pressure chamber a secondary pressure chamber separated and in the transition area from Pendulum body to the pendulum footbridge formed a throttled drain becomes.
  • the main pressure chamber is advantageously at least one Outflow channel connected.
  • the inner radius of the Ring area of the outer rotor circular shape and no after to provide internally directed segments. Furthermore, it is very cheap if the attachment points, such as screws, for fastening the lid radially are arranged outside the pressure chambers.
  • FIG. 1 shows a cylinder head 100 with hydraulic devices 102, 104 for continuously variable adjustment of not shown here Inlet and exhaust camshaft (s) of a multi-cylinder internal combustion engine in frontal view.
  • s Inlet and exhaust camshaft
  • the device 102, 104 allows an adjustment of the camshaft relative to the crankshaft and thus the timing of the cam this wave actuated valves, with advantages in particular with respect on emissions, fuel consumption, torque history and Performance development result.
  • the device 102, 104 is in the drive train arranged the camshaft drive, wherein a drive of the camshaft starting from the crankshaft via an outer rotor 114, 116 and a to this relatively rotatable, not visible in the present view, Internal rotor takes place.
  • Each adjusting device 102, 104 is in a suitably designed Room 106, 108 of the cylinder head and includes the cup-shaped outer rotor 114, 116, with which a drive wheel, such as Sprocket 110, 112, to the output of the crankshaft drive connected is.
  • a drive wheel such as Sprocket 110, 112
  • the outer rotor 114, 116 is the rotation with the camshaft connected, not visible in the present view
  • inner rotor taken to the outer rotor 114, 116 relative between two Drehendlagen is rotatable and which front side a hub portion 118, 120 is assigned.
  • the cup-shaped interior of the outer rotor 114, 116 is closed by means of a screwed lid 122, 124.
  • a cylinder head cover to cover the entire arrangement is a cylinder head cover, not shown here provided, which rests tightly on the peripheral flange 126.
  • This relatively rotatable inner rotor is in Figure 2 in perspective Illustration shown.
  • a ring portion 208 and a Bottom portion 210 having outer rotor 202 is one with the Bottom portion 210 of the outer rotor 202 rotatably connected drive wheel, like sprocket 206, provided.
  • drive wheel like sprocket 206
  • the outer rotor 202 is relative to this rotatable, rotatably connected to a camshaft inner rotor 204th added.
  • the inner rotor has a plurality, in the present case six, rotor blades 212, 214, 216, 218, 220, 222, which with their outer ends at the inner radius of Ring portion 208 of the outer rotor 202 at relative rotation between Outer rotor 202 and inner rotor 204 sliding, but tight, abut.
  • cylindrical shell-shaped pendulum head guides in which the Pendulum heads of pendulum 224, 226, 228, 230, 232, 234 swiveling are arranged, whose pendulum feet in Pendelfußnuten 236, 238, 240, 242, 244, 246 of the outer rotor 202 pivotally mounted and radially displaceable are.
  • the pendulum 224, 226, 228, 230, 232, 234 close with the Rotor blades 212, 214, 216, 218, 220, 222 pressurizable Main pressure chambers and lie in the Drehendlagen as shown on the Rotor blades 212, 214, 216, 218, 220, 222;
  • Each pendulum 224, 226, 228, 230, 232, 234 are thus associated with two main pressure chambers.
  • a relative rotation of inner 204 and outer rotor 202 is by a Pressure differential in the one pendulum 224, 226, 228, 230, 232, 234 associated main pressure chambers achieved, with adjustment angle and Adjustment can be controlled by appropriate pressure gradients.
  • FIG. 3 A detailed view of an arranged between rotor blades 312, 314, pivotally mounted pendulum 326 and a pressurizable Main 376, 374 and secondary pressure chamber 380 shows Figure 3.
  • the pivotable in the inner rotor 304 mounted cylindrical pendulum head 362 ensures a very long, precisely defined sealing gap with good sealing and allows at the same time a high angle of rotation between inner 304 and outer rotor 302 of up to 25-45 °, in particular of about 35 °.
  • the pendulum 326 For pivoting and radial slidable mounting of the pendulum 326 in the Pendelfußnut 338 of Outer rotor 302, the pendulum 326 has a cylindrical, frontally flattened pendulum foot 360 on, so by applying the Pendulum foot 260 to the Pendelfußnut 338 in the direction of the main pressure chamber with lower pressure even in case of possible wear of the Construction of very high pressures with minimized leakage losses is guaranteed.
  • the pendulum 326 between pendulum head 362 and Pendulum foot 360 one with pendulum head 362 and pendulum foot 360 by means of webs 366, 368 connected, cylindrical-drop-shaped pendulum body 364, wherein the transition from pendulum body 364 to the pendelfuß solutionen web 366th small, when applied to the rotor blades 314, 312 a throttle edge forming Radii and the transition from pendulum body 364 to pendulum head side Bridge has 368 large radii.
  • the rotor blades 312, 314 have one with the contour of a pendulum 326th corresponding contact surface, wherein upon movement in the direction the Drehendlagen in the transition region 372 from the pendulum body 364 to pendulum-head-side web 368 from the main pressure chamber 374 a secondary pressure chamber 380 separated and in the transition region 370 from the shuttle 364 to pendulum footbridge 366 a throttled drain is formed.
  • a throttled drain is formed with increasing abutment of the pendulum 326 with an associated rotor blade, such as the rotor blade 314 shown in the figure.
  • Main pressure chamber 374 and the secondary pressure chamber 380 reach one minimum and that between pendulum body 326 and rotor blades 312 enclosed main pressure chamber 376 reaches a maximum size. Also upon reaching the minimum size, the main pressure space 374 includes small remaining volume, whereas that of Mautikraum 380 enclosed volume is at least approximately close to zero.
  • the arrangement according to the invention ensures a damped application the pendulum 224, 226, 228, 230, 232, 234, 326 to the corresponding Wing sides in the rotary end positions, by applying the pendulum 224, 226, 228, 230, 232, 234, 326 to the rotor blades 212, 214, 216, 218, 220, 222, 312, 314 of the inner rotor 204, 304 not only the main pressure chambers Form "squeeze chambers" in which the oil must be displaced, respectively but also secondary pressure chambers, such as that shown in FIG Secondary pressure chamber 380, to be separated, the additional pressure pad form.
  • a pressure reduction from the secondary pressure chamber 380 is strong throttled over in the transition region 370 from the pendulum body 364 to pendulum side web 366 formed Abiserspalt in the associated Main pressure chamber 374.
  • the main pressure chambers have, as in FIG. 2 illustrated perspective view partially visible, respectively Drain holes 248, 250 on.
  • Inner 204, 304 and outer rotor 202, 302 are in at least one Rotational end position, especially in a previous valve actuation assigned rotary end position, locked against each other, so that For example, a start of the internal combustion engine in this preferred position, the also serves as a reference position takes place.
  • the locking device comprises a guided in a broader rotor blade 222 axially movable Locking bolt 252, which in the locking position in the Bottom portion 210 of the cup-shaped outer rotor 202 engages.
  • the Preferred position is, especially if the pressure chambers are not are pressurized, by means of a preloaded spring, which at least indirectly on the outer rotor 202 on the one hand and on the inner rotor 204th on the other hand supports, ingestible.
  • the adjusting device is in essentially made of steel, but the arrangement is also very good for the implementation of a, for example, aluminum and / or magnesium-based lightweight construction concept, in particular, since in the Drehendlagen a material-saving, damped system of pendulum the rotor blades is guaranteed. Furthermore, the arrangement offers special Advantages in terms of manufacturing, as the inner radius of the ring area 208 of the outer rotor 202, 302, on which the rotor blades 212, 214, 216, 218, 220, 222, 312, 314 sliding with their outer ends, but dense abut, is circular in shape and no inward Has segments. In particular, in a lightweight construction is effectively prevents component distortion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Hydraulic Motors (AREA)
EP05007186A 2004-04-23 2005-04-01 Dispositif hydraulique pour la variation continue du calage d'arbre à cames Ceased EP1589196A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004019770 2004-04-23
DE200410019770 DE102004019770A1 (de) 2004-04-23 2004-04-23 Hydraulische Einrichtung zur stufenlos variablen Nockenwellenverstellung

Publications (2)

Publication Number Publication Date
EP1589196A2 true EP1589196A2 (fr) 2005-10-26
EP1589196A3 EP1589196A3 (fr) 2008-08-06

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EP05007186A Ceased EP1589196A3 (fr) 2004-04-23 2005-04-01 Dispositif hydraulique pour la variation continue du calage d'arbre à cames

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EP (1) EP1589196A3 (fr)
DE (1) DE102004019770A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1762706A3 (fr) * 2005-09-13 2007-05-30 Delphi Technologies, Inc. Déphaseur d'arbre à cames du type à palettes avec angle de déphasage accru, verrouillage en positon intermédiaire et alimentation propre en huile

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4542012A3 (fr) * 2023-10-19 2025-06-04 Cummins, Inc. Déphaseur d'arbre à cames pour moteurs à combustion interne

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19961567A1 (de) 1999-12-21 2001-07-05 Guenther Beez Hydraulische Vorrichtung zur stufenlos variablen Nockenwellenverstellung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19819995A1 (de) * 1998-05-05 1999-11-11 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
JP2000130117A (ja) * 1998-10-27 2000-05-09 Aisin Seiki Co Ltd 弁開閉時期制御装置
DE10055770A1 (de) * 2000-11-10 2002-05-23 Bayerische Motoren Werke Ag Verfahren für den Betrieb eines Ventils für eine hydraulische Verstelleinheit
DE10104038A1 (de) * 2001-01-31 2002-08-01 Bayerische Motoren Werke Ag Vorrichtung zum Verdrehen einer Exzenterwelle eines Ventiltriebs
US6445608B1 (en) * 2001-09-10 2002-09-03 Ramtron International Corporation Ferroelectric random access memory configurable output driver circuit
DE10150856B4 (de) * 2001-10-15 2005-08-11 Ina-Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE10218201C1 (de) * 2002-04-24 2003-10-30 Porsche Ag Nockenwellenversteller für eine veränderbare Ventilsteuerung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19961567A1 (de) 1999-12-21 2001-07-05 Guenther Beez Hydraulische Vorrichtung zur stufenlos variablen Nockenwellenverstellung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1762706A3 (fr) * 2005-09-13 2007-05-30 Delphi Technologies, Inc. Déphaseur d'arbre à cames du type à palettes avec angle de déphasage accru, verrouillage en positon intermédiaire et alimentation propre en huile
US7421989B2 (en) 2005-09-13 2008-09-09 Delphi Technologies, Inc. Vane-type cam phaser having increased rotational authority, intermediate position locking, and dedicated oil supply

Also Published As

Publication number Publication date
EP1589196A3 (fr) 2008-08-06
DE102004019770A1 (de) 2005-11-10

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