EP1076762B1 - Dispositif de deplacement hydraulique de l'angle de rotation d'un arbre par rapport a une roue d'entrainement - Google Patents

Dispositif de deplacement hydraulique de l'angle de rotation d'un arbre par rapport a une roue d'entrainement Download PDF

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Publication number
EP1076762B1
EP1076762B1 EP99923415A EP99923415A EP1076762B1 EP 1076762 B1 EP1076762 B1 EP 1076762B1 EP 99923415 A EP99923415 A EP 99923415A EP 99923415 A EP99923415 A EP 99923415A EP 1076762 B1 EP1076762 B1 EP 1076762B1
Authority
EP
European Patent Office
Prior art keywords
webs
inner part
pressure
cellular wheel
pressure chambers
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
EP99923415A
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German (de)
English (en)
Other versions
EP1076762A1 (fr
Inventor
Bernd Niethammer
Andreas Knecht
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
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Application filed by Dr Ing HCF Porsche AG, Hydraulik Ring GmbH filed Critical Dr Ing HCF Porsche AG
Publication of EP1076762A1 publication Critical patent/EP1076762A1/fr
Application granted granted Critical
Publication of EP1076762B1 publication Critical patent/EP1076762B1/fr
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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
    • 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
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a device for the hydraulic rotation angle adjustment of a shaft to a drive wheel, in particular the camshaft of an internal combustion engine, according to the Genus of the main claim.
  • Such a device is known for example from US-A 4,858,572.
  • an inner part is rotatably connected to the end of the camshaft, which has on its outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially displaceably.
  • This inner part is surrounded by a cellular wheel which has a plurality of cells which can be acted upon hydraulically and which are subdivided by the wings into two pressure spaces acting against one another. By pressurizing these pressure chambers, depending on the pressure difference, the cellular wheel can be rotated relative to the inner part and thus to the camshaft.
  • a hydraulically actuated piston is guided in two radial bores in defined angular positions in the cellular wheel, which piston can be inserted into a radial recess of the inner part in the assigned end position of the device.
  • These pistons are acted upon by compression spring elements in the direction of the inner part and can be displaced in the opposite direction by hydraulic action on the bores in the inner ring.
  • the device is to be locked in one of its two end positions, as long as the pressure for acting on the pressure chambers does not reach a defined level. Only when a certain pressure level is reached are the pistons pushed back against the action of the compression springs and allow the inner part to be rotated relative to the cell wheel.
  • Such a device is intended, inter alia, to avoid rattling noises when the internal combustion engine starts up, which occur as a result of changing moment loads when the internal combustion engine starts up and operates.
  • a device for the hydraulic rotation angle adjustment of a camshaft to its drive wheel is also known, in which the inner part is provided with fixed, radially extending webs. Pressure springs are clamped between the webs of the inner part and the opposite webs or walls of the cellular wheel, which are intended to move the inner part relative to the cellular wheel into one of the two end positions when the pressure is reduced.
  • JP 2-241914 which is listed as prior art in US Pat. No. 5,215,046, shows a so-called gearbox axial camshaft adjuster, which, in contrast to Generic device for relative change in rotational position only one Pressure chamber is formed, the pressurization of a spring element counteracts.
  • a separate hydraulic damping chamber is provided opposite the pressure chamber is sealed to adjust the camshaft.
  • the integrated hydraulic damping is in a particularly advantageous manner in the form of a hydraulically effective damping throttle.
  • Integrated damping that becomes effective when the end position is approached can be achieved in a particularly advantageous manner if between the webs of Inner part and the webs of the cellular wheel, a throttle chamber is formed in the pressure medium is enclosed before the end position is reached.
  • Throttle chamber formed between the relatively moving components is, an appropriate angular assignment of the Damping begins or begins when a defined position is reached Damping can be set. This can be ensured in a particularly advantageous manner be that the adjustment process undamped over the largest possible angular range he follows.
  • a particularly advantageous one with regard to the mechanical load on the components End position damping results if the throttle chamber has a defined one Throttle gap can be relieved. This can be done in the Pressure chamber enclosed pressure medium relatively strong when approaching the end position exit throttled so that excessive damping is avoided. This is done by Appropriate training of the sealing gap continues to ensure that the mechanical limited end position can be reached in any case. Adverse spring effects can thus be effectively prevented.
  • Such a throttle chamber can be designed in a particularly advantageous manner be, if in one of the adjacent webs a depression and in the another web a corresponding extension is formed.
  • the projections dip into the recess in adjacent recesses, so that the opposite wall areas through their overlap the throttle chamber complete or form the throttle gap.
  • 1 shows the camshaft of an internal combustion engine the free end of which the inner part 2 of an adjusting device 3 is arranged in a rotationally fixed manner.
  • This inner part 2 is in this embodiment with four radially arranged webs 4a to 4d provided.
  • the inner part is encompassed by a cellular wheel 5, which is not closer to shown way is connected to the crankshaft of the internal combustion engine and consequently acts as a drive wheel.
  • the cellular wheel 5 has four inwardly projecting radial webs 6a to 6d, between which four cells are formed, the through the webs of the inner part in two pressure spaces 7a to 7d and 8a to 8d are divided. These pressure chambers are designed so that the sum of the hydraulic effective areas in both adjustment directions is the same.
  • the pressure spaces 7a to 7d are each via a radial bore 9a to 9d in the inner part with an annular groove 10 on the Camshaft 1 connected.
  • the pressure spaces 8a to 8d are in an analogous manner via radial Bores 11a to 11d in the inner part with a second annular groove 12 in the camshaft connected.
  • the radial bores 9a to 9d and 11a to 11d are each so arranged that they each in the foot area of the webs 4a to 4d in the corresponding Pressure rooms open.
  • the two ring grooves 10 and 12 are each one in the Camshaft extending pressure channel 13 and 14 connected. These pressure channels 13 and 14 are in a manner known per se via a camshaft bearing 15 with one each Control line 16 or 17 connected.
  • the two control lines 16 and 17 are with a control valve 18, which is designed, for example, as a 4/3-way valve. This control valve 18 is also with a pressure medium pump 19 and Oil tank 20 connected.
  • switch position II neutral position of the control valve 18 shown in FIG. 1
  • the connections to the two control lines 16 and 17, the pressure medium pump 19 and the oil tank 20 is closed on one side.
  • the Adjustment device clamped hydraulically and keeps the respective relative Position assignment of inner wheel and cellular wheel at.
  • switch position I of the control valve 18 are the pressure chambers 7a to 7d via the bores 9a to 9d, the annular groove 10 Pressure channel 14 and the pressure line 17 connected to the pressure medium pump 19 and accordingly pressurized.
  • the pressure spaces 8a to 8d are over the bores 11a to 11d, the annular groove 12, the pressure channel 13 and the pressure line 16 connected to the oil tank 20 and thus relieved.
  • the inner part 2 is covered by the Pressurizing the pressure spaces 7a to 7d in the viewing direction chosen in FIG. 1 rotated counterclockwise to cell wheel 5. This twist will at the same time the pressure medium located in the pressure chambers 8a to 8d in addition to Oil tank displaced.
  • the cellular wheel 5 and the inner part 2 are each constructed symmetrically.
  • the embodiment of the embodiment shown in FIGS. 3a to 3c is simplified Crosspieces of the inner part and the cellular wheel only using the example of a crosspiece or the represented by this limited pressure space, but also applies to the same other webs or pressure rooms.
  • Figures 3a to 3c and following description only the approximation to the end position analogous to Switch position I shown and described. Approaching the opposite End position (switch position III) takes place analogously.
  • These depressions 21, 22 extend over the entire Width (in the axial direction) of the respective web.
  • the depressions 21, 22 extend extend approximately in the radial direction over the inner third of the respective web and up to the end face 23 or up to the adjacent peripheral surface 24 of the inner part 2.
  • a projection 25 or 26 is formed on the webs 4a to 4d of the inner part 2 .
  • These projections 25 and 26 are in their position so coordinated that they with the respective adjacent recesses 21 and 22nd correspond.
  • the projections 25 act in each case with the depressions 22 and the projections 26 together with the depressions 21 of the respectively adjacent web.
  • the projections 25 and 26 also extend over the entire width (in axial Direction) of the webs. In contrast to the specializations, they are sufficient in this Embodiment, however, not up to the peripheral surface of the inner part, so that their Bottom sides 27 are spaced apart from these.
  • the tops 28 of the protrusions 25, 26 have a small radial distance from the shoulders 29 of the depressions 21 and 22, so that the projections when approaching the end position - as can be seen in Fig. 3b - under Formation of a throttle gap 32 can dip into the wells.
  • the pressure spaces 8a to 8d are each in two partial pressure spaces 30 and 31 divided.
  • the partial pressure space 30 located at the foot of the webs 4a to 4d of the inner part 2 is then still with the respectively opening into the pressure chamber 11a to 11d in connection.
  • the radially outer partial pressure chamber 31, which acts as a throttle chamber is by the overlap of the top 28 and the shoulder 29 of the partial pressure chamber 30 largely separated and is only over the emerging throttle gap 32 in connection with this.
  • the pressure medium located in the partial pressure chamber 31 can be further rotation to the end position (direct abutment of the webs against each other, Fig.
  • the throttling effect that occurs depends besides the effect of the viscosity, above all on the height and length of the throttle gap from.
  • the length of the throttle gap increases with increasing coverage.
  • the height of the throttle gap depends on the distance between the top 28 and the shoulder 29. By adjusting the height of the throttle gap, the throttling effect on the be matched to the respective operating conditions. In this embodiment the top and shoulder run largely parallel.
  • the throttling effect increases at least approximately proportionally to increase the coverage or to extend the throttle gap, i.e. with increasing approach to the end position.
  • To vary the height of the throttle gap so that the influence of the change in length of the Throttle gap is increased or decreased. This can be done for example by wedge-like Arrange the top relative to the shoulder.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention concerne un dispositif de modification relative de l'angle de rotation de l'arbre à cames (1) d'un moteur à combustion interne par rapport à sa roue d'entraînement. Ce dispositif comprend principalement une partie intérieure (2) munie d'entretoises (4a à 4b) ou d'ailettes, qui est montée de manière à tourner dans une roue cellulaire (5). Cette dernière (5) comporte plusieurs entretoises (6a à 6b) réparties en périphérie, qui sont subdivisées en deux chambres de pression (7a à 7d, 8a à 8d) par les entretoises (4a à 4d) ou les ailettes de la partie intérieure (2), la modification de l'angle de rotation étant produite par leur sollicitation en pression ou leur décompression. A l'approche d'une position terminale, le mouvement de déplacement est amorti hydrauliquement par des éléments amortisseurs intégrés. Ces éléments amortisseurs sont formés par l'interaction des entretoises (4a à 4d, 6a à 6d) (5) qui se rapprochent mutuellement, de la partie intérieure (2) et de la roue d'entraînement (5).

Claims (9)

  1. Dispositif de variation relative de l'angle de rotation de l'arbre à cames d'un moteur à combustion interne par rapport à une roue d'entraínement, comportant une partie intérieure (2) reliée solidairement en rotation à l'arbre à cames (1), qui comporte des entretoises ou ailettes (4a à 4d) s'étendant au moins approximativement radialement, et comportant une roue cellulaire (5) entraínée qui comporte plusieurs cellules réparties sur le pourtour et limitées par des entretoises (6a à 6d), lesquelles cellules sont divisées en deux chambres de pression (7a à 7d, 8a à 8d) par les entretoises ou ailettes de la partie intérieure, guidées mobiles angulairement, dont l'alimentation en pression ou la décharge de pression fait tourner l'arbre à cames, par les entretoises ou pales, entre deux positions terminales par rapport à la roue cellulaire, caractérisé en ce que la variation de la position de rotation est amortie hydrauliquement avant que soit atteinte une des deux positions terminales, par des moyens d'amortissement (21, 22 ; 25, 26 ; 32) intégrés, les moyens d'amortissement étant réalisés en tant qu'organes d'étranglement et d'amortissement (32).
  2. Dispositif selon la revendication 1, caractérisé en ce qu'entre les entretoises (4a à 4d) de la partie intérieure et les entretoises (6a à 6d) de la roue cellulaire, il est formé une chambre d'étranglement (31) dans laquelle est enfermé le fluide sous pression, avant que ne soit atteinte la position terminale.
  3. Dispositif selon la revendication 2, caractérisé en ce que la chambre d'étranglement (30, 31) est déchargée hydrauliquement par une fente d'étranglement (32).
  4. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la chambre d'étranglement est formée par un renfoncement (21, 22) dans l'une des entretoises de la partie intérieure ou de la roue cellulaire, et une saillie (25, 26) adjacente dans l'entretoise voisine de la roue cellulaire de la partie intérieure.
  5. Dispositif selon l'une des revendications précédentes, caractérisé en ce que les chambres de pression (7a à 7d, 8a à 8d) sont partagées en deux chambres partielles de pression (30, 31) entre lesquelles est formée la chambre d'étanchéité (32), à l'approche de la position terminale respective.
  6. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la fente d'étanchéité (32) est formée par une surface périphérique (29) du renfoncement et une surface périphérique (28) de la saillie.
  7. Dispositif selon l'une des revendications précédentes, caractérisé en ce que l'opération d'amortissement s'effectue sur le côté écoulement de l'alimentation hydraulique des chambres de pression.
  8. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la roue cellulaire est réalisée en tant que composant fritté, et en ce que les saillies respectivement les renfoncements sont réalisés en même temps pendant l'opération de frittage.
  9. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la partie intérieure est réalisée en tant que composant fritté, et en ce que les saillies respectivement les renfoncements sont réalisés en même temps pendant l'opération de frittage.
EP99923415A 1998-05-05 1999-04-14 Dispositif de deplacement hydraulique de l'angle de rotation d'un arbre par rapport a une roue d'entrainement Expired - Lifetime EP1076762B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19819995 1998-05-05
DE19819995A DE19819995A1 (de) 1998-05-05 1998-05-05 Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
PCT/EP1999/002504 WO1999057423A1 (fr) 1998-05-05 1999-04-14 Dispositif de deplacement hydraulique de l'angle de rotation d'un arbre par rapport a une roue d'entrainement

Publications (2)

Publication Number Publication Date
EP1076762A1 EP1076762A1 (fr) 2001-02-21
EP1076762B1 true EP1076762B1 (fr) 2002-06-26

Family

ID=7866702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99923415A Expired - Lifetime EP1076762B1 (fr) 1998-05-05 1999-04-14 Dispositif de deplacement hydraulique de l'angle de rotation d'un arbre par rapport a une roue d'entrainement

Country Status (8)

Country Link
US (1) US6390043B1 (fr)
EP (1) EP1076762B1 (fr)
JP (1) JP4422899B2 (fr)
KR (1) KR100562444B1 (fr)
CN (1) CN1113155C (fr)
DE (2) DE19819995A1 (fr)
ES (1) ES2175978T3 (fr)
WO (1) WO1999057423A1 (fr)

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JP3447601B2 (ja) * 1999-02-05 2003-09-16 本田技研工業株式会社 内燃機関の動弁制御装置
EP1164255B1 (fr) * 2000-06-16 2004-03-31 Dr.Ing. h.c.F. Porsche Aktiengesellschaft Appareil pour régler la phase entre un arbre à cames et une roue motrice d'un moteur à combustion interne
DE10112206A1 (de) * 2001-03-14 2002-09-26 Porsche Ag Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad
US6866013B2 (en) * 2002-04-19 2005-03-15 Borgwarner Inc. Hydraulic cushioning of a variable valve timing mechanism
DE10320639A1 (de) * 2003-04-22 2004-11-11 Hydraulik-Ring Gmbh Nockerwellenversteller für Fahrzeuge, vorzugsweise für Kraftfahrzeuge
US6883480B1 (en) * 2003-12-19 2005-04-26 Hydraulik-Ring Gmbh Camshaft adjuster for internal combustion engines of motor vehicles
DE102004019770A1 (de) * 2004-04-23 2005-11-10 Bayerische Motoren Werke Ag Hydraulische Einrichtung zur stufenlos variablen Nockenwellenverstellung
DE102006019607B4 (de) * 2006-04-25 2008-01-31 Hydraulik-Ring Gmbh Nockenwellenversteller
DE102007058491A1 (de) * 2007-12-05 2009-06-10 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP4905843B2 (ja) * 2010-02-23 2012-03-28 株式会社デンソー バルブタイミング調整装置
US8555836B2 (en) * 2010-12-10 2013-10-15 Delphi Technologies, Inc. Electric drive camshaft phaser with torque rate limit at travel stops
US9341089B2 (en) 2014-04-04 2016-05-17 RB Distribution, Inc. Camshaft phaser
SE539977C2 (en) * 2016-06-08 2018-02-20 Scania Cv Ab Variable cam timing phaser utilizing hydraulic logic element
DE102018107351A1 (de) 2017-03-28 2018-10-04 Borgwarner Inc., Patent Department Geschalteter pufferanschlag
US10371241B1 (en) * 2018-06-22 2019-08-06 Baoxiang Shan Stress-wave actuator and reducer
CN114321194B (zh) * 2021-12-30 2023-05-12 新疆金风科技股份有限公司 联轴节装置

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DE19756016A1 (de) * 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad

Also Published As

Publication number Publication date
KR20010043317A (ko) 2001-05-25
DE59901863D1 (de) 2002-08-01
ES2175978T3 (es) 2002-11-16
CN1113155C (zh) 2003-07-02
WO1999057423A1 (fr) 1999-11-11
EP1076762A1 (fr) 2001-02-21
CN1299437A (zh) 2001-06-13
KR100562444B1 (ko) 2006-03-20
JP2002513883A (ja) 2002-05-14
DE19819995A1 (de) 1999-11-11
US6390043B1 (en) 2002-05-21
JP4422899B2 (ja) 2010-02-24

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