EP1155223B1 - Moteur a combustion interne multicylindre pourvu de soupapes d'echange de gaz actionnees par des actionneurs electromagnetiques - Google Patents

Moteur a combustion interne multicylindre pourvu de soupapes d'echange de gaz actionnees par des actionneurs electromagnetiques Download PDF

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Publication number
EP1155223B1
EP1155223B1 EP00904881A EP00904881A EP1155223B1 EP 1155223 B1 EP1155223 B1 EP 1155223B1 EP 00904881 A EP00904881 A EP 00904881A EP 00904881 A EP00904881 A EP 00904881A EP 1155223 B1 EP1155223 B1 EP 1155223B1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
actuators
lift valves
inlet
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
EP00904881A
Other languages
German (de)
English (en)
Other versions
EP1155223A1 (fr
Inventor
Adelbert Grudno
Albert HÖRL
Volker Warnecke
Ferdinand Loebbering
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
Siemens AG
Original Assignee
Bayerische Motoren Werke AG
Siemens 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, Siemens AG filed Critical Bayerische Motoren Werke AG
Publication of EP1155223A1 publication Critical patent/EP1155223A1/fr
Application granted granted Critical
Publication of EP1155223B1 publication Critical patent/EP1155223B1/fr
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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means

Definitions

  • the invention relates to a multi-cylinder internal combustion engine with electromagnetic Actuators actuated and the inlet and the outlet of the Gas exchange globe valves controlling cylinder combustion chambers.
  • the environment is referred to DE 196 11 547 A1.
  • An electromagnetic lift valve actuating device for an internal combustion engine also called electromagnetic actuator
  • electromagnetic actuator because of the Freedom in terms of valve timing, i.e. regarding the respective Opening and closing times of the globe valves have immense advantages, however must be relatively to actuate, especially to open the globe valve high forces are applied, which is a certain minimum size of magnetic coils and requires anchors.
  • the basically known actuators at all in one today usual cylinder head for example of a motor vehicle To accommodate the internal combustion engine. This problem occurs even more intensely Internal combustion engines based on two or more intake valves or exhaust valves own each cylinder.
  • the working capacity of an electromagnetic actuating a globe valve Actuator is directly determined by the size of the magnet coils arranged in the actuator (including the laminated core and the one between the solenoids oscillating armature, which ultimately acts on the lift valve) certainly. This means that an actuator does less work must also have a smaller cross-sectional area - perpendicular to the axis direction the lift valve to be operated considered - can have as one Actuator that has to do a larger job. I agree this connection is in the characterizing features of the claim 1 reproduced.
  • FIG. 1 shows a cross section through the cylinder head of an internal combustion engine according to the invention, while in FIG is shown. All features described in more detail can be essential to the invention, although it should be expressly pointed out beforehand that, although the invention is explained below using a four-cylinder in-line internal combustion engine, the present invention can of course also be implemented on an internal combustion engine of a different type or with a different number of cylinders ,
  • each cylinder has two intake lift valves 3 and two exhaust lift valves 4 assigned via which the gas exchange of the cylinder is controlled will, i.e. Fresh gas gets into the respective one via the inlet lift valves Cylinder combustion chambers, while the burned exhaust gas via the exhaust lift valves 4 is discharged.
  • All inlet lift valves 3 of the internal combustion engine are arranged one behind the other in a row in the direction of the longitudinal axis 2 of the internal combustion engine. likewise, all of the exhaust lift valves 4 of the internal combustion engine are arranged one behind the other in a further row in the direction of the longitudinal axis 2 of the internal combustion engine.
  • the inlet lift valves 3 are on the right side and the outlet lift valves 4 are on the left side. 2
  • the inlet lift valves 3 are in the upper half of the figure, ie above the longitudinal axis 2 running through the center of the internal combustion engine or cylinder head 1
  • the outlet lift valves are in the lower half of the figure, ie below the longitudinal axis 2.
  • FIG. 1 the inlet lift valves 3 are on the right side and the outlet lift valves 4 are on the left side.
  • the lift valves 3, 4 are actuated by electromagnetic actuators 13, 14 assigned to them, the detailed structure of which is not explained in detail here, since on the one hand this is known to the person skilled in the art and on the other hand can be designed essentially as described in the aforementioned DE 196 11 547 A1 shown.
  • These actuators 13, 14 are located above the respective lift valves 3, 4 and, like these, are opposite the vertical axis 5 of the internal combustion engine, on the bottom 1a of the cylinder head 1 facing the internal combustion engine crankcase (as well as on the drawing level in the illustration below) Fig. 2 ) is vertical, slightly inclined to the outside. With their undersides 13a and 14a, the actuators 13 and 14 are thus perpendicular to the axial directions 3 'and 4' of the lift valves 3 and 4, respectively.
  • a so-called cross-sectional area 13b or 14b of the actuators 13 or 14 is defined, which runs perpendicular to the axial direction 3 'or 4' and thus parallel to the respective underside 13a or 13b of an actuator 13 or 14.
  • FIG. 1 of course, only the width of the cross-sectional area 13 or 14 running perpendicular to the longitudinal axis 2 of the internal combustion engine can be shown.
  • This measure of the width of the cross-sectional area 13 or 14 is designated by the letter B in FIG.
  • the measured in the direction of the longitudinal axis 2 of the longitudinal dimension L of each actuator 13 and 14 is apparent from Figure 2, which - as also shows Fig.2 - a substantially rectangular cross-sectional surface 13b or 14b has.
  • the distance x a between the two cylinder outlet lift valves 4 measured in the direction of the longitudinal axis 2 of the internal combustion engine is equal to the distance x e between the two cylinder inlet lift valves 3 measured in the direction of the longitudinal axis of the internal combustion engine 2. Accordingly, it is possible to design the actuators 14 of the exhaust lift valves 4 and the actuators 13 of the intake lift valves 3 in such a way that the actuators 13 and 14 have an essentially identical longitudinal dimension L (measured in the direction of the longitudinal axis 2 of the internal combustion engine).
  • the width dimension B of the actuators 13 assigned to the inlet lift valves 3 is smaller than the width dimension B of the actuators 14 assigned to the outlet lift valves 4. Accordingly, the cross-sectional area 13b is the Actuators 13 are smaller than the cross-sectional area 14b of the actuators 14.
  • inlet actuators 13 may be less than that of the so-called outlet actuators 14, after that of the former in the course of a Opening movement of the inlet lift valves 4 work to be performed is less than that of the latter in the course of an opening movement the exhaust lift valves 4 work to be performed.
  • this measure is fundamentally desired by one Identical parts concept deviated, i.e. distinguish the outlet actuators 14 differ from the inlet actuators 13, however, on the other hand, with this Measure significant advantages in terms of the space required achieved.
  • a spark plug dome 6 provided between the plane of all exhaust lift valves 4 running in the direction of the longitudinal axis 2 of the internal combustion engine and the corresponding plane of all intake lift valves 3 for receiving a spark plug, not shown in the figure, is at least slightly parallel to the inlet actuators 13 with its longitudinal axis 6a inclined towards, the intersection of this longitudinal axis with the cylinder combustion chamber, not shown, is substantially in the center of the combustion chamber.
  • each cylinder of the multi-cylinder internal combustion engine has such a spark plug dome 6, although such is only shown in FIG. 2 for the first (right-hand) cylinder.
  • the longitudinal axis 6a of the spark plug dome 6 coming into congruence with the longitudinal axis of the assembled spark plug is thus slightly inclined towards the inlet actuators 13 with respect to the vertical axis 5 of the internal combustion engine, as can be seen in particular from FIG .
  • This spark plug dome 6, viewed in the direction of the longitudinal axis 2 of the internal combustion engine, is essentially arranged between the two intake lift valves 3 (and between the two exhaust lift valves 4) of each internal combustion engine cylinder. It is obvious that this measure also leads to a reduction in the overall width of the internal combustion engine ( measured perpendicular to the longitudinal axis 2 in FIG. 2 and perpendicular to the vertical axis 5 in FIG. 1 ).
  • the in the actuators 13, 14 The amount of heat generated is thus largely via the underside 13a or 14a to the cylinder head 1 and in this via the in the Pressure oil channels 7 led lubricant oil discharged from the internal combustion engine. A part of this lubricating oil guided in the pressure oil channels 7 can also passed through the electromagnetic actuators 13, 14 not only for lubrication purposes, but also for a reinforced one Cooling the same (not shown in figures).

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)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (7)

  1. Moteur à combustion interne multicylindre comportant des soupapes d'échange de gaz (3, 4) pour l'admission et l'échappement de la chambre de combustion des cylindres, commandé par des actionneurs électromagnétiques (13, 14),
    caractérisé en ce que
    la surface (13b) de la section des actionneurs (13) des soupapes d'admission (3), perpendiculaire à la direction axiale (3', 4') des soupapes (3, 4), est inférieure à la section correspondante (14b) des actionneurs (14) des soupapes d'échappement (4).
  2. Moteur à combustion interne selon la revendication 1,
    dans lequel les soupapes d'admission (3) et les soupapes d'échappement (4) sont placées l'une derrière l'autre dans une rangée dans la direction de l'axe longitudinal (2) du moteur à combustion interne,
    caractérisé en ce que
    la largeur (B) des actionneurs d'admission (13), mesurée dans le plan de la surface de la section (13b, 14b) des actionneurs, perpendiculairement à l'axe longitudinal (2) du moteur, est inférieure à la largeur (B) des actionneurs d'échappement (14).
  3. Moteur à combustion interne selon l'une quelconque des revendications 1 ou 2 avec chaque fois deux soupapes d'admission (3) et deux soupapes d'échappement (4) par cylindre,
    caractérisé en ce que
    la distance (xa) mesurée dans la direction de l'axe longitudinal (2) du moteur à combustion interne entre les deux soupapes d'échappement (4) du cylindre est égale à la distance correspondante (xe) entre les deux soupapes d'admission (3) du cylindre.
  4. Moteur à combustion interne selon l'une quelconque des revendications précédentes,
    caractérisé par
    un dôme à bougie d'allumage (6) prévu entre le plan des soupapes d'échappement (4) et celui des soupapes d'admission (3) pour recevoir une bougie d'allumage dont l'axe longitudinal (6a) est incliné au moins légèrement par rapport aux actionneurs d'admission (13).
  5. Moteur à combustion interne selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    des canaux d'huile sous pression (7) qui passent essentiellement dans la direction de l'axe longitudinal (2) du moteur, à travers la culasse (1), sont prévus au voisinage de la face inférieure (13a, 14a) des actionneurs (13, 14), surfaces par lesquelles ceux-ci s'appliquent contre la culasse (1).
  6. Moteur à combustion interne selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    à proximité de la face inférieure (13a, 14a) des actionneurs (13, 14), faces par lesquelles ceux-ci s'appliquent contre la culasse (1), on a une accumulation relativement importante de matière formant la culasse (1).
  7. Moteur à combustion interne selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    à proximité de la face inférieure (13a, 14a) des actionneurs (13, 14), faces par lesquelles ceux-ci s'appuient contre la culasse (1), on a dans la culasse (1) des cavités de liquide de refroidissement pour du liquide de refroidissement traversant la culasse (1).
EP00904881A 1999-02-24 2000-01-07 Moteur a combustion interne multicylindre pourvu de soupapes d'echange de gaz actionnees par des actionneurs electromagnetiques Expired - Lifetime EP1155223B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19907850 1999-02-24
DE19907850A DE19907850C2 (de) 1999-02-24 1999-02-24 Mehrzylindrige Brennkraftmaschine mit von elektromagnetischen Aktuatoren betätigten Gaswechsel-Hubventilen
PCT/EP2000/000064 WO2000050741A1 (fr) 1999-02-24 2000-01-07 Moteur a combustion interne multicylindre pourvu de soupapes d'echange de gaz actionnees par des actionneurs electromagnetiques

Publications (2)

Publication Number Publication Date
EP1155223A1 EP1155223A1 (fr) 2001-11-21
EP1155223B1 true EP1155223B1 (fr) 2002-12-11

Family

ID=7898622

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00904881A Expired - Lifetime EP1155223B1 (fr) 1999-02-24 2000-01-07 Moteur a combustion interne multicylindre pourvu de soupapes d'echange de gaz actionnees par des actionneurs electromagnetiques

Country Status (5)

Country Link
US (1) US6568358B1 (fr)
EP (1) EP1155223B1 (fr)
JP (1) JP2002543316A (fr)
DE (2) DE19907850C2 (fr)
WO (1) WO2000050741A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20010570A1 (it) * 2001-09-20 2003-03-20 Magneti Marelli Powertrain Spa Sistema elettromagnetico per il comando delle valvole di un motore
DE10317644A1 (de) 2003-04-17 2004-11-04 Fev Motorentechnik Gmbh Elektromagnetischer Aktuator mit unsymmetrischer Magnetkreisauslegung zur Betätigung eines Gaswechselventils
US7089894B2 (en) * 2003-10-14 2006-08-15 Visteon Global Technologies, Inc. Electromechanical valve actuator assembly
US7353563B2 (en) 2004-07-09 2008-04-08 Tacony Corporation Vacuum cleaner height adjustment

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5113805A (en) * 1989-12-12 1992-05-19 Isuzu Ceramics Research Institute Co., Ltd. Variable-cycle engine
US5193492A (en) * 1990-11-13 1993-03-16 Isuzu Ceramics Research Institute Co., Ltd. 2-4 cycle change-over engine and its control system
DE4225329A1 (de) 1992-07-31 1993-02-18 Dreyer Dietmar Ventilansteuerungseinrichtung fuer den einsatz in verbrennungsmotoren
JPH07301105A (ja) * 1994-05-06 1995-11-14 Honda Motor Co Ltd 内燃機関の動弁装置
US5941202A (en) * 1994-11-01 1999-08-24 Hyundai Motor Company Device for varying valve timing
US5517951A (en) * 1994-12-02 1996-05-21 Paul; Marius A. Two stroke/four stroke engine
JP3134724B2 (ja) * 1995-02-15 2001-02-13 トヨタ自動車株式会社 内燃機関の弁駆動装置
DE19611547A1 (de) * 1996-03-23 1997-09-25 Bayerische Motoren Werke Ag Elektromagnetische Betätigungsvorrichtung für Brennkraftmaschinen-Hubventile
JPH1073011A (ja) * 1996-08-30 1998-03-17 Fuji Heavy Ind Ltd 電磁動弁駆動制御装置
DE19714496B4 (de) * 1997-04-08 2008-04-03 Bayerische Motoren Werke Ag Elektromagnetische Betätigungsvorrichtung für ein Brennkraftmaschinen-Hubventil
US6176208B1 (en) * 1997-07-03 2001-01-23 Nippon Soken, Inc. Electromagnetic valve driving apparatus
DE19801396C1 (de) * 1998-01-16 1999-03-04 Daimler Benz Ag Betätigungsvorrichtung für ein Gaswechselventil in einer Brennkraftmaschine
DE19814803A1 (de) * 1998-04-02 1999-10-14 Daimler Chrysler Ag Hubkolbenbrennkraftmaschine
US6269784B1 (en) * 2000-04-26 2001-08-07 Visteon Global Technologies, Inc. Electrically actuable engine valve providing position output

Also Published As

Publication number Publication date
WO2000050741A1 (fr) 2000-08-31
DE19907850A1 (de) 2000-09-14
DE50000915D1 (de) 2003-01-23
EP1155223A1 (fr) 2001-11-21
DE19907850C2 (de) 2002-08-01
US6568358B1 (en) 2003-05-27
JP2002543316A (ja) 2002-12-17

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