EP3006684B1 - Commande de soupape a commande mecanique et systeme de commande de soupape pouvant etre commande - Google Patents

Commande de soupape a commande mecanique et systeme de commande de soupape pouvant etre commande Download PDF

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Publication number
EP3006684B1
EP3006684B1 EP15180950.6A EP15180950A EP3006684B1 EP 3006684 B1 EP3006684 B1 EP 3006684B1 EP 15180950 A EP15180950 A EP 15180950A EP 3006684 B1 EP3006684 B1 EP 3006684B1
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EP
European Patent Office
Prior art keywords
valve drive
mechanically controllable
controllable valve
drive assembly
pivot lever
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.)
Active
Application number
EP15180950.6A
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German (de)
English (en)
Other versions
EP3006684A1 (fr
Inventor
Christoph Sadowski
Dr. Michael Breuer
Stefan Moormann
Dr. Karsten Grimm
Martin Lauterbach
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Pierburg GmbH
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Pierburg GmbH
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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
    • 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
    • F01L13/0063—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 modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot

Definitions

  • the invention relates to a mechanically controllable valve train arrangement for at least one multi-cylinder row of an internal combustion engine having at least two cylinders, in each of which at least one gas exchange valve is provided, each of which acts on a transmission arrangement by means of an end face, wherein the transmission arrangement is movably mounted in the cylinder head by means of bearing means and wherein the transmission arrangement is in operative connection with a Ventilhubverstell sexual and a camshaft, wherein the Ventilhubverstell responded rotatable adjusting members having at least one eccentric member which acts on the transmission assembly against a biasing force of a spring member, such that different Ventilhubpositionen are adjustable, the Ventilhubverstell observed at least one actuator for a cylinder such that various valve lift positions, such as zero stroke, partial lift and full stroke adjust are bar.
  • Valve trains and such valve train arrangements are well known from the prior art.
  • the EP 638 706 A1 to control or regulate the valve lift a rotatably mounted in a cylinder head eccentric shaft, which acts on the transmission arrangement such that in a simple way valve strokes between 0 and can be set to a maximum.
  • the combustion process can be easily adapted to the respective operating state of the internal combustion engine.
  • it is from the DE 10 2004 003 327 A1 known to provide adjusting members in a valve train assembly that can be adjusted independently with the aim of individual cylinders for to shut down certain operating conditions.
  • the EP 1 760 278 A2 a valve train known, which has an eccentric member having different curves, in particular for the partial stroke and the full stroke. A zero-stroke curve is also made possible by the adjustment.
  • valve trains / valve train arrangements have the disadvantage that an adjustment of the valve lift via the Exzenterorgankurve must be very accurate.
  • variability of the valve lift settings in the known valve train arrangements in a partial cylinder shutdown is very limited, which in turn leads to increased fuel consumption and thus also to higher emissions.
  • Solutions for valve train arrangements are known in which the adjusting member has at least one eccentric member in the circumferential direction. But even hereby is a fast adjustment at an engine speed of, for example, 3000 / min within a base circle phase of the camshaft from maximum lift to minimum stroke can not be realized.
  • the object of the invention is therefore to provide a valve train or a valve train arrangement, the / o.g. Disadvantage in a simple and inexpensive way avoids.
  • each cylinder is associated with at least one actuator, wherein the actuators are operatively connected via a reduction gear transmission with the adjusting member, wherein the gear transmission of a spur gear and a worm gear is constructed, wherein a Schneckenradwelle is provided and wherein Adjusting member is at least partially designed as a worm wheel ..
  • a particularly advantageous embodiment is provided in that the reduction is between 5/1 and 10/1.
  • a small cost-effective actuator with low inertia can be used.
  • this reduces the problem of inertia even further, since the Aktuatorflamiere can reduce.
  • the worm wheel shaft is mounted above and below the adjusting member.
  • the adjusting member may advantageously have an eccentric member designed as a control cam.
  • each transmission arrangement has at least one pivot lever arrangement and at least one rocker arm, wherein a pivot lever of the pivot lever assembly engages with an end face on the gas exchange valve and the rocker arm is in operative connection with the Ventilhubverstell issued and a camshaft and over a working curve on the pivot lever attacks.
  • FIG. 1 shows an embodiment of a valve train assembly 10 according to the invention of a 4-cylinder in-line engine with a gas inlet side 12 and a gas outlet side 14, which are each assigned in a known manner a cylinder, not shown.
  • gas inlet and outlet valves have been omitted. In the following description should be limited to a gas inlet side 12.
  • the gas inlet valves, not shown are associated in a known manner pivot lever assemblies 16, 18, 20, 22, 24, 26, 28, 30, wherein in each case a pivot lever assembly is in operative connection with a gas exchange valve.
  • the pivot lever arrangements 16, 18, 20, 22, 24, 26, 28, 30 are part of eight transmission arrangements 32, 34, 36, 38, 40, 42, 44, 46, on each of which a pivot lever arrangement 16, 18, 20, 22, 24, 26, 28, 30 is assigned.
  • the transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 are mounted in a known manner in the cylinder head by means not shown bearing means.
  • the transmission assemblies 32, 34, 36, 38, 40, 42, 44, 46 in a known manner with a camshaft 48 in operative connection.
  • each transmission assembly 32, 34, 36, 38, 40, 42, 44, 46 by adjusting members 50, 52, 54, 56, 58, 60, 62, 64, each having an eccentric member 51 (see FIG.
  • a Ventilhubverstell disturbing 66 can be controlled such that a lesser, higher valve lift or even a shutdown of the gas inlet valves is adjustable.
  • the eccentric member 51 of each adjusting member 50, 52, 54, 56, 58, 60, 62, 64 designed as a control cam, wherein two adjusting members 50, 52, 54, 56, 58, 60, 62, 64 on a Shaft section 68, 70, 72, 74 are provided.
  • each shaft section 68, 70, 72, 74 is in operative connection with an actuator 76, 78, 80, 82.
  • the Ventilhubverstell familiar 66 is in the present embodiment with respect to the gas inlet side 12 thus four actuators 76, 78, 80, 82, four shaft sections 68, 70, 72, 74, each with two adjusting members 50, 52, 54, 56, 58, 60, 62, 64, wherein the shaft portions 68, 70, 72, 74, as shown in FIG. 2 explained, transmission technology with the actuators 76, 78, 80, 82 are coupled.
  • a transmission assembly 32 has a pivot lever assembly 16 with a pivot lever 84 and a rocker arm 86, wherein the pivot lever 84 engages in a known manner with an end face on a gas inlet valve and the rocker arm 86 is in operative connection with the Ventilhubverstell responded 66 and the camshaft 48.
  • the adjusting member 50 of the Ventilhubverstell aggr 66 engages against a biasing force of a spring, not shown on an engaging member 88 (for example, a roller) of the rocker arm 86 at.
  • the rocker arm 86 engages with a working curve 90 not shown (see FIG. 2 ) on the pivot lever 84 at.
  • FIG. 2 shows now in a side view of the Sprinthielungsan Aunt 32.
  • the power is transmitted to the pivot lever assembly 16 due to the camshaft rotation of the camshaft 48.
  • a cam 104 of the camshaft 48 engages the roller 102 at.
  • the actuator 76 is provided, which is operatively connected via a reduction gear transmission 106 with the shaft portion 68 and thus with the adjusting member 50.
  • the gear transmission 106 consists in the present embodiment of a straight spur gear 108 and a worm gear 110, wherein a worm wheel 112 is provided, the screw gear via a worm gear 114 indirectly via the shaft portion 68 with the adjusting member 50 is engaged. In the present embodiment, this ensures a reduction of 7: 1. Characterized in that the worm wheel shaft 112 is mounted above and below the adjusting member 50 via bearing means 116, 118, the flexural rigidity is increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (5)

  1. Système de commande de soupape à commande mécanique destiné à au moins une rangée à plusieurs cylindres d'un moteur à combustion interne, comprenant au moins deux cylindres, dans lesquels au moins une soupape d'échange de gaz est respectivement prévu, sur laquelle agit, respectivement, un ensemble de transmission (32, 34, 36, 38, 40, 42, 44, 46) par une face avant, ledit ensemble de transmission (32, 34, 36, 38, 40, 42, 44, 46) étant supporté de manière à être mobil dans la tête du cylindre par des moyens de support, et ledit ensemble de transmission (32, 34, 36, 38, 40, 42, 44, 46) étant en liaison active avec un moyen d'ajustage de la levée des soupapes (66) et un arbre à cames (48), ledit moyen d'ajustage de la levée des soupapes (66) comprenant des organes d'ajustage (50, 52, 54, 56, 58, 60, 62, 64) rotatifs avec au moins un organe excentrique (51) agissant sur ledit ensemble de transmission (32) à l'encontre d'une force de précontrainte d'un organe de ressort, de sorte que différentes positions de levée des soupapes peuvent être ajustées, ledit moyen d'ajustage de la levée des soupapes (66) comprenant au moins un actionneur (76, 78, 80, 82), caractérisé en ce que chaque cylindre est associé à au moins un actionneur (76, 78, 80, 82), lesdits actionneurs (76, 78, 80, 82) étant en liaison active avec ledit organe d'ajustage (50, 52, 54, 56, 58, 60, 62, 64) par un engrenage réducteur (106), ledit engrenage (106) étant formé par un engrenage cylindrique à denture droite (108) et un engrenage à vis sans fin (110), un arbre de vis sans fin (112) étant prévu, et ledit organe d'ajustage (50) étant au moins partiellement réalisé en forme d'une vis sans fin (114).
  2. Système de commande de soupape à commande mécanique selon la revendication 1, caractérisé en ce que le taux de réduction se situe entre 5/1 et 10/1.
  3. Système de commande de soupape à commande mécanique selon la revendication 2, caractérisé en ce que ledit arbre de vis sans fin (112) est supporté au-dessus et au-dessous dudit organe d'ajustage (50, 52, 54, 56, 58, 60, 62, 64) par des moyens de support (116, 118).
  4. Système de commande de soupape à commande mécanique selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit organe d'ajustage (50, 52, 54, 56, 58, 60, 62, 64) comprend un organe excentrique (50) en forme d'un came de commande.
  5. Système de commande de soupape à commande mécanique selon l'une quelconque des revendications 1 à 4, caractérisé en ce que chaque ensemble de transmission (32, 34, 36, 38, 40, 42, 44, 46) comprend au moins un ensemble de levier pivotant (16, 18, 20, 22, 24, 26, 28, 30) et au moins un levier basculant (86), un levier pivotant (84) dudit ensemble de levier pivotant (16, 18, 20, 22, 24, 26, 28, 30) engageant la soupape d'échange de gaz par une face avant, et ledit levier basculant (86) étant en liaison active avec ledit moyen d'ajustage de la levée des soupapes (66) et un arbre à cames (48) et engageant ledit levier basculant (84) par une courbe de travail (90).
EP15180950.6A 2014-10-02 2015-08-13 Commande de soupape a commande mecanique et systeme de commande de soupape pouvant etre commande Active EP3006684B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014114396.5A DE102014114396A1 (de) 2014-10-02 2014-10-02 Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung

Publications (2)

Publication Number Publication Date
EP3006684A1 EP3006684A1 (fr) 2016-04-13
EP3006684B1 true EP3006684B1 (fr) 2017-08-02

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EP (1) EP3006684B1 (fr)
DE (1) DE102014114396A1 (fr)
ES (1) ES2642861T3 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1426568A1 (fr) * 2002-12-05 2004-06-09 Toyota Jidosha Kabushiki Kaisha Système et dispositif électrique de commande de soupapes d'un moteur à combustion interne

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0638706A1 (fr) 1993-08-05 1995-02-15 Bayerische Motoren Werke Aktiengesellschaft Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne
DE19548389A1 (de) * 1995-12-22 1997-06-26 Siemens Ag Verstellvorrichtung für den Hubverlauf eines Gaswechselventils einer Brennkraftmaschine
DE10106921A1 (de) * 2001-02-15 2002-08-22 Bayerische Motoren Werke Ag Verfahren zum Synchronisieren der Füllung von Zylindern einer Brennkraftmaschine, insbesondere eines Hubkolben-Verbrennungsmotors
DE10213081A1 (de) * 2002-03-20 2003-10-02 Hydraulik Ring Gmbh Ventilsteuerung zur Einstellung des Hubes von Ventilen in Kraftfahrzeugen
DE10235401A1 (de) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb
DE102004003327A1 (de) 2004-01-22 2005-09-29 Entec Consulting Gmbh Vorrichtung zur variablen Ventilhubverstellung von Gaswechselventilen einer Verbrennungskraftmaschine
EP1710402B1 (fr) * 2003-12-18 2013-06-19 Toyota Jidosha Kabushiki Kaisha Mecanisme de distributeur variable
DE102005040959A1 (de) 2005-08-30 2007-03-08 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb für eine Brennkraftmaschine
JP2007127117A (ja) * 2005-10-04 2007-05-24 Masaaki Yoshikawa ４ストローク内燃機関の動弁系装置
JP4259512B2 (ja) * 2005-11-14 2009-04-30 トヨタ自動車株式会社 内燃機関の可変動弁装置
DE102006002133A1 (de) * 2006-01-17 2007-07-19 Bayerische Motoren Werke Ag Ventiltrieb zur hubvariablen Betätigung eines Gaswechselventils einer Brennkraftmaschine
DE102006033559A1 (de) * 2006-07-20 2008-01-24 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb für eine Brennkraftmaschine
DE102010048709B4 (de) 2010-10-19 2013-01-03 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
JP2012149609A (ja) * 2011-01-20 2012-08-09 Denso Corp バルブリフト調節装置のアクチュエータ
DE102011009416B4 (de) * 2011-01-25 2016-11-03 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbare Ventiltriebanordnung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1426568A1 (fr) * 2002-12-05 2004-06-09 Toyota Jidosha Kabushiki Kaisha Système et dispositif électrique de commande de soupapes d'un moteur à combustion interne

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Publication number Publication date
ES2642861T3 (es) 2017-11-20
EP3006684A1 (fr) 2016-04-13
DE102014114396A1 (de) 2016-04-07

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