EP1155223A1 - Multicylinder internal combustion engine with gas flow lift valves actuated by electromagnetic actuators - Google Patents

Multicylinder internal combustion engine with gas flow lift valves actuated by electromagnetic actuators

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Publication number
EP1155223A1
EP1155223A1 EP00904881A EP00904881A EP1155223A1 EP 1155223 A1 EP1155223 A1 EP 1155223A1 EP 00904881 A EP00904881 A EP 00904881A EP 00904881 A EP00904881 A EP 00904881A EP 1155223 A1 EP1155223 A1 EP 1155223A1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
actuators
lift valves
cylinder
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.)
Granted
Application number
EP00904881A
Other languages
German (de)
French (fr)
Other versions
EP1155223B1 (en
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/en
Application granted granted Critical
Publication of EP1155223B1 publication Critical patent/EP1155223B1/en
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 gas exchange valves actuated by electromagnetic actuators and controlling the inlet and the outlet of the cylinder combustion chambers.
  • gas exchange valves actuated by electromagnetic actuators and controlling the inlet and the outlet of the cylinder combustion chambers.
  • An electromagnetic globe valve actuation device for an internal combustion engine also called an electromagnetic actuator
  • an electromagnetic actuator has immense advantages because of the freedom with regard to the valve timing, ie with respect to the respective opening and closing times of the globe valves, but relatively high forces have to be applied to actuate, in particular to open the globe valve , which requires a certain minimum size of solenoids and armatures.
  • measures are now to be shown which contribute to solving the problem just described.
  • the resulting negative pressure supports an opening movement of the inlet lift valves.
  • the exhaust stroke valves when the exhaust stroke valves are opened, they must be opened against the excess pressure still prevailing in the cylinder at this point, which makes it clear that more work has to be done when an exhaust stroke valve is opened than when the valve is opened Inlet lift valves.
  • the working capacity of an electromagnetic actuator actuating a stroke valve is determined directly by the size of the magnet coils arranged in the actuator (including the laminated core and the armature which oscillates between the magnet coils and which ultimately acts on the stroke valve).
  • 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 with reference to a four-cylinder in-line internal combustion engine, the present invention naturally also applies to an internal combustion engine of a different type or with a different number of cylinders is feasible.
  • Reference number 1 denotes the cylinder head of a four-cylinder reciprocating internal combustion engine, ie in the direction of the longitudinal axis 2 of the internal combustion engine (this longitudinal axis 2 is perpendicular to the plane), four internal combustion engine cylinders are arranged one behind the other.
  • Each cylinder is assigned two intake lift valves 3 and two exhaust lift valves 4, via which the gas exchange of the cylinder is controlled, ie fresh gas reaches the respective cylinder combustion chambers via the intake lift valves, 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, and likewise all outlet 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.
  • the inlet lift valves 3 are in the upper half of the figure, i.e. above the longitudinal axis 2 running through the center of the internal combustion engine or the cylinder head 1, and the exhaust stroke valve in the lower half of the figure, i.e. below the longitudinal axis 2.
  • 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 essentially be designed as described in the introduction 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 (and on the drawing level in the illustration) 2) is vertical, arranged slightly inclined outwards. 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 shows only the width of the cross-sectional area 13 or 14 running perpendicular to the longitudinal axis 2 of the internal combustion engine.
  • This measure of the width of the cross-sectional area 13 or 14 is designated by the letter B in FIG. 2 also shows the longitudinal dimension L of each actuator 13 or 14 measured in the direction of the longitudinal axis 2, which - as also shown in FIG. 2 - has an essentially rectangular cross-sectional area 13b or 14b.
  • 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 measured in the direction of the longitudinal axis 2 of the internal combustion engine 3. 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) . As can be seen particularly clearly from FIG. 1 but also from FIG.
  • the width dimension B of the actuators 13 assigned to the inlet lift valves 3 is, however, 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.
  • the cross-sectional area 13b of the so-called inlet actuators 13 can be smaller than that of the so-called outlet actuators 14 after the one of the former mentioned in the course of an opening movement of the inlet Lift valves 4 work or power to be performed is less than the work or power to be performed by the latter in the course of an opening movement of the outlet lift valve 4.
  • This measure deviates from a principle of the same parts concept, i.e.
  • the outlet actuators 14 differ from the inlet actuators 13, but on the other hand significant advantages are achieved with this measure in terms of the space required.
  • the electromagnetic actuators 13 and 14 assigned to the respective lift valves 3 and 4 are dimensioned in each case with regard to the work to be performed by them and in particular also with regard to their external geometric dimensions, ie here with regard to their cross-sectional areas 13b and 14b . If - as explained above and at the beginning - a smaller installation space is required for the inlet actuators 13, which have a smaller cross-sectional area 13b and in particular a smaller width dimension B, than for the larger or wider outlet actuators 14, on the other hand, this gain in installation space can otherwise be used or the whole of the Internal space as a whole, the installation space required can be reduced accordingly.
  • 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 intake Actuators 13 inclined, the intersection of this longitudinal axis with the cylinder combustion chamber, not shown, is essentially in the center of the combustion chamber.
  • each cylinder of the multi-cylinder internal combustion engine has such a spark plug dome 6, although one is shown in FIG. 2 only for the first (right-hand) cylinder.
  • the longitudinal axis 6a of the spark plug dome 6 which coincides with the longitudinal axis of the assembled spark plug (not shown) 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 amount of heat generated in the actuators 13, 14 is thus largely discharged to the cylinder head 1 via the underside 13a or 14a thereof and discharged into the cylinder head 1 via the lubricating oil of the internal combustion engine guided in the pressure oil channels 7.
  • Part of this lubricating oil, which is guided in the pressure oil channels 7, can also be passed through the electromagnetic actuators 13, 14, not only for lubrication purposes, but also for increased cooling thereof (not shown in the figure).

Abstract

The invention relates to a multicylinder internal combustion engine with gas flow lift valves actuated by electromagnetic actuators and controlling the intake and the exhaust of the cylinder combustion chambers. The cross-sectional area of the actuators allocated to the intake lift valves which is perpendicular to the axial direction of the lift valves is smaller than the cross-sectional area of the actuators allocated to the exhaust lift valves. If the intake lift valves and the exhaust lift valves are arranged in series one after the other in the direction of the longitudinal axis of the internal combustion engine, the width of the intake actuators measured in the plane of the actuator cross-sectional area and perpendicular to the longitudinal axis of the internal combustion engine is smaller than that of the exhaust actuators. If two intake lift valves and two exhaust lift valves each are provided per cylinder, the distance between the two cylinder exhaust lift valves measured in the direction of the longitudinal axis of the internal combustion engine equals the distance between the two cylinder intake lift valves. An ignition spark provided between the plane of the exhaust lift valves and the plane of the intake lift valves is at least slightly inclined towards the intake actuators with its longitudinal axis.

Description

Mehrzylindrige Brennkraftmaschine mit von elektromagnetischen Aktuatoren betätigten Gaswechsel-HubventilenMulti-cylinder internal combustion engine with gas exchange lift valves actuated by electromagnetic actuators
Die Erfindung betrifft eine mehrzylindrige Brennkraftmaschine mit von elektromagnetischen Aktuatoren betätigten und den Einlaß sowie den Auslaß der Zylinder-Brennräume steuernden Gaswechsel-Hubventilen. Zum technischen Umfeld wird beispielshalber auf die DE 196 11 547 A1 verwiesen.The invention relates to a multi-cylinder internal combustion engine with gas exchange valves actuated by electromagnetic actuators and controlling the inlet and the outlet of the cylinder combustion chambers. With regard to the technical environment, reference is made, for example, to DE 196 11 547 A1.
Eine elektromagnetische Hubventil-Betätigungsvorrichtung für eine Brennkraftmaschine, auch elektromagnetischer Aktuator genannt, hat wegen der Freiheit hinsichtlich der Ventilsteuerzeiten, d.h. hinsichtlich des jeweiligen Öffnungs- und Schließzeitpunktes der Hubventile immense Vorteile, jedoch müssen zum Betätigen, insbesondere zum Öffnen des Hubventiles relativ hohe Kräfte aufgebracht werden, was eine gewisse Mindestgröße von Magnetspulen und Anker erforderlich macht. Als Folge hiervon ist es äußerst schwierig, die grundsätzlich bekannten Aktuatoren überhaupt in einem heute üblichen Zylinderkopf beispielsweise einer ein Kraftfahrzeug antreibenden Brennkraftmaschine unterzubringen. Noch intensiver tritt dieses Problem bei Brennkraftmaschinen auf, die zwei oder mehr Einlaßventile oder Auslaßventile je Zylinder besitzen. Mit der vorliegenden Erfindung sollen nun Maßnahmen aufgezeigt werden, die zur Lösung der soeben geschilderten Problematik beitragen. Die Lösung dieser Aufgabe ist dadurch gekennzeichnet, daß die senkrecht zur Achsrichtung der Hubventile liegende Querschnittsfläche der den Einlaß- Hubventilen zugeordneten Aktuatoren geringer ist als die dementsprechende Querschnittsfläche der den Auslaß-Hubventilen zugeordneten Aktuatoren. Vorteilhafte Aus- und Weiterbildungen sind Inhalt der Unteransprüche.An electromagnetic globe valve actuation device for an internal combustion engine, also called an electromagnetic actuator, has immense advantages because of the freedom with regard to the valve timing, ie with respect to the respective opening and closing times of the globe valves, but relatively high forces have to be applied to actuate, in particular to open the globe valve , which requires a certain minimum size of solenoids and armatures. As a result, it is extremely difficult to accommodate the basically known actuators in a cylinder head that is common today, for example, an internal combustion engine driving a motor vehicle. This problem occurs even more intensely in internal combustion engines which have two or more intake valves or exhaust valves per cylinder. With the present invention, measures are now to be shown which contribute to solving the problem just described. The solution to this problem is characterized in that the cross-sectional area of the actuators assigned to the inlet lift valves, which is perpendicular to the axial direction of the lift valves, is smaller than the corresponding cross-sectional area of the actuators assigned to the outlet lift valves. Advantageous training and further education are included in the subclaims.
Erfindungsgemäß wird vom bisher üblichen Gleichteilekonzept abgewichen, d.h. es wird vorgeschlagen, anstelle der bisher üblichen Vorgehensweise, wobei für die Einlaß-Hubventile sowie die Auslaß-Hubventiie gleich dimensionierte Aktuatoren vorgesehen waren, nunmehr die Aktuatoren hinsichtlich ihrer Leistungsfähigkeit und somit auch hinsichtlich ihrer insbesondere geo- metrischen Dimensionen an die jeweils zu betätigenden Hubventile anzupassen. Es wurde nämlich erkannt, daß für eine Betätigung eines Einlaß- Hubventiles einer Brennkraftmaschine geringere Kräfte erforderlich sind als für eine Betätigung eines Brennkraftmaschinen-Auslaß-Hubventiles. Dies hat die Ursache darin, daß eine Öffnungsbewegung der Einlaß-Hubventile mit einem Ansaugtakt der Brennkraftmaschine einhergeht, in welchem das Zylindervolumen bspw. im Falle einer Hubkolben-Brennkraftmaschine durch den (sozusagen nach unten gerichteten) Saughub des Zylinder-Kolbens vergrößert wird. Der dabei entstehende Unterdruck unterstützt eine Öffnungsbewegung der Einlaß-Hubventile. Hingegen müssen bei einer Öffnungsbe- wegung der Auslaß-Hubventiie diese gegen den zu diesem Zeitpunkt noch im Zylinder herrschenden Überdruck geöffnet werden, wodurch klar verständlich wird, daß mit dem Öffnen eines Auslaß-Hubventiles eine größere Arbeit verrichtet werden muß, als mit einem Öffnen des Einlaß-Hubventiles. Das Arbeitsvermögen eines ein Hubventii betätigenden elektromagnetischen Aktuators wird direkt durch die Größe der im Aktuator angeordneten Magnetspulen (inklusive des Blechpaketes sowie des zwischen den Magnetspulen oszillierend bewegten Ankers, welcher letztlich auf das Hubventil einwirkt) bestimmt. Dies bedeutet, daß ein Aktuator, der eine geringere Arbeit verrichten muß, auch eine geringere Querschnittsfläche - senkrecht zur Achsrichtung des zu betätigenden Hubventiles betrachtet - besitzen kann, als ein Aktuator, der eine demgegenüber größere Arbeit verrichten muß. Genau dieser Zusammenhang ist in den kennzeichnenden Merkmalen des An- spruchs 1 wiedergegeben.According to the invention, there is a departure from the previously common parts concept, ie it is proposed, instead of the previously usual procedure, with actuators of the same size being provided for the intake and exhaust valves, and the actuators with regard to their performance and thus also with regard to their geo- adapt metric dimensions to the respective globe valves to be operated. It has been recognized that less force is required to actuate an intake lift valve of an internal combustion engine than to actuate an internal combustion engine exhaust lift valve. This is due to the fact that an opening movement of the inlet lift valves is accompanied by an intake stroke of the internal combustion engine, in which the cylinder volume is increased, for example in the case of a reciprocating piston internal combustion engine, by the (so to speak downward) suction stroke of the cylinder piston. The resulting negative pressure supports an opening movement of the inlet lift valves. On the other hand, when the exhaust stroke valves are opened, they must be opened against the excess pressure still prevailing in the cylinder at this point, which makes it clear that more work has to be done when an exhaust stroke valve is opened than when the valve is opened Inlet lift valves. The working capacity of an electromagnetic actuator actuating a stroke valve is determined directly by the size of the magnet coils arranged in the actuator (including the laminated core and the armature which oscillates between the magnet coils and which ultimately acts on the stroke valve). This means that an actuator, which has to do less work, can also have a smaller cross-sectional area - perpendicular to the axial direction of the lift valve to be actuated - than an actuator, which has to do a larger job. Exactly this relationship is shown in the characterizing features of claim 1.
Unter Ausnutzung dieser Kenntnis kann dann die Brennkraftmaschine bzw. genauer deren Zylinderkopf (bzw. ein Bestandteil desselben), in welchem die Hubventile sowie die diese betätigenden Aktuatoren angeordnet sind, weiter hinsichtlich einer raumsparenden Bauweise ausgebildet werden. Dies sowie weitere vorteilhafte Ausgestaltungen geht auch aus dem im folgenden erläuterten bevorzugten Ausführungsbeispiel der Erfindung hervor, von welchem Figur 1 einen Querschnitt durch den Zylinderkopf einer erfindungsgemäßen Brennkraftmaschine zeigt, während in Figur 2 eine Aufsicht (gemäß Pfeil X aus Fig.1 ) auf den Zylinderkopf dargestellt ist. Erfindungswesentlich können dabei sämtliche näher beschriebenen Merkmale sein, wobei vorab ausdrücklich darauf hingewiesen sei, daß, wenngleich im folgenden die Erfindung anhand einer vierzylindrigen Reihen-Brennkraftmaschine erläutert wird, selbstverständlich die vorliegende Erfindung auch an einer Brennkraft- maschine einer anderen Bauart oder mit einer anderen Zylinderzahl realisierbar ist.Using this knowledge, the internal combustion engine or, more precisely, its cylinder head (or a component thereof), in which the lift valves and the actuators actuating them are arranged, can be further developed in terms of a space-saving design. This, as well as further advantageous refinements, can also be seen from the preferred exemplary embodiment of the invention explained below, of which 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 with reference to a four-cylinder in-line internal combustion engine, the present invention naturally also applies to an internal combustion engine of a different type or with a different number of cylinders is feasible.
Mit der Bezugsziffer 1 ist der Zylinderkopf einer hier vierzylindrigen Hubkolben-Brennkraftmaschine bezeichnet, d.h. in Richtung der Längsachse 2 der Brennkraftmaschine (diese Längsachse 2 steht in Fig.1 senkrecht zur Zei- chenebene) sind vier Brennkraftmaschinen-Zylinder hintereinander angeordnet. Jedem Zylinder sind zwei Einlaß-Hubventile 3 sowie zwei Auslaß- Hubventile 4 zugeordnet, über welche der Gaswechsel des Zylinders gesteuert wird, d.h. über die Einlaß-Hubventile gelangt Frischgas in die jeweili- gen Zylinder-Brennräume, während das verbrannte Abgas über die Auslaß- Hubventile 4 abgeführt wird.Reference number 1 denotes the cylinder head of a four-cylinder reciprocating internal combustion engine, ie in the direction of the longitudinal axis 2 of the internal combustion engine (this longitudinal axis 2 is perpendicular to the plane), four internal combustion engine cylinders are arranged one behind the other. Each cylinder is assigned two intake lift valves 3 and two exhaust lift valves 4, via which the gas exchange of the cylinder is controlled, ie fresh gas reaches the respective cylinder combustion chambers via the intake lift valves, while the burned exhaust gas via the exhaust Lift valves 4 is discharged.
Sämtliche Einlaß-Hubventile 3 der Brennkraftmaschine sind in einer Reihe in Richtung der Brennkraftmaschinen-Längsachse 2 hintereinander angeord- net, ebenso sind sämtliche Auslaß-Hubventiie 4 der Brennkraftmaschine in einer weiteren Reihe in Richtung der Brennkraftmaschinen-Längsachse 2 hintereinander angeordnet. In der Darstellung nach Fig.1 befinden sich die Einlaß-Hubventile 3 rechtsseitig und die Auslaß-Hubventiie 4 linksseitig. In der Darstellung naph Fig.2 befinden sich die Einlaß-Hubventile 3 in der obe- ren Bildhälfte, d.h. oberhalb der durch die Mitte der Brennkraftmaschine bzw. des Zylinderkopfes 1 verlaufenden Längsachse 2, und die Auslaß-Hubventiie in der unteren Bildhälfte, d.h. unterhalb der Längsachse 2. Dabei sind in der Darstellung nach Fig.2 lediglich die Einlaß-Hubventile 3 und die Auslaß- Hubventile 4 des ersten (hier rechtsseitig außen) liegenden Zylinders der vierzylindrigen Brennkraftmaschine dargestellt, und auch das lediglich in vereinfachter Weise in Form der als Punkt (wegen der Aufsicht) dargestellten jeweiligen Ventilachse, die bzw. der der Einfachheit halber ebenfalls mit der jeweiligen Bezugsziffer 3 bzw. 4 bezeichnet ist. In der Darstellung nach Fig.1 hingegen ist die Achsrichtung der Hubventile 3 bzw. 4 mit den Bezugsziffern 3' bzw. 4' versehen.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, and likewise all outlet 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. In the illustration according to FIG. 1, the inlet lift valves 3 are on the right side and the outlet lift valves 4 are on the left side. In the illustration according to FIG. 2, the inlet lift valves 3 are in the upper half of the figure, i.e. above the longitudinal axis 2 running through the center of the internal combustion engine or the cylinder head 1, and the exhaust stroke valve in the lower half of the figure, i.e. below the longitudinal axis 2. Only the intake lift valves 3 and the exhaust lift valves 4 of the first (here on the right-hand side outside) cylinder of the four-cylinder internal combustion engine are shown in the illustration according to FIG. 2, and also only in a simplified manner in the form of as a point (because of the supervision) shown respective valve axis, which is also designated for the sake of simplicity with the respective reference number 3 or 4. In the illustration according to FIG. 1, however, the axial direction of the lift valves 3 or 4 is provided with the reference numerals 3 'or 4'.
Betätigt werden die Hubventile 3, 4 durch diesen zugeordnete elektromagnetische Aktuatoren 13, 14, deren detaillierter Aufbau hier nicht näher erläutert wird, da dieser einerseits dem Fachmann bekannt ist und anderer- seits im wesentlichen so gestaltet sein kann, wie in der eingangs genannten DE 196 11 547 A1 gezeigt. Diese Aktuatoren 13, 14 befinden sich dabei oberhalb der jeweiligen Hubventile 3, 4 und sind ebenso wie diese gegenüber der Hochachse 5 der Brennkraftmaschine, die auf dem dem nicht dargestellten Brennkraftmaschinen-Kurbelgehäuse zugewandten Boden 1a des Zylinderkopfes 1 (sowie auf der Zeichenebene in der Darstellung nach Fig.2) senkrecht steht, geringfügig nach außen geneigt angeordnet. Mit ihren Unterseiten 13a bzw. 14a stehen die Aktuatoren 13 bzw. 14 somit senkrecht auf den Achsrichtungen 3' bzw. 4' der Hubventile 3 bzw. 4.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 essentially be designed as described in the introduction 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 (and on the drawing level in the illustration) 2) is vertical, arranged slightly inclined outwards. 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.
Für die weiteren Erläuterungen wird eine sog. Querschnittsfläche 13b bzw. 14b der Aktuatoren 13 bzw. 14 definiert, die senkrecht zur Achsrichtung 3' bzw. 4' und somit parallel zur jeweiligen Unterseite 13a bzw. 13b eines Ak- tuators 13 bzw. 14 verläuft. In Fig.1 kann dabei selbstverständlich nur die senkrecht zur Brennkraftmaschinen-Längsachse 2 verlaufende Breite der Querschnittsfläche 13 bzw. 14 dargestellt werden. Dieses Maß der Breite der Querschnittsfläche 13 bzw. 14 ist in Fig.2 mit dem Buchstaben B bezeichnet. Aus Fig.2 wird daneben auch das in Richtung der Längsachse 2 gemessene Längsmaß L jedes Aktuators 13 bzw. 14 ersichtlich, der - wie ebenfalls Fig.2 zeigt - eine im wesentlichen rechteckförmige Querschnittsfläche 13b bzw. 14b besitzt.For the further explanations, 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 . In 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. 2 also shows the longitudinal dimension L of each actuator 13 or 14 measured in the direction of the longitudinal axis 2, which - as also shown in FIG. 2 - has an essentially rectangular cross-sectional area 13b or 14b.
Wie Fig.2 zeigt ist der in Richtung der Brennkraftmaschinen-Längsachse 2 gemessene Abstand xa zwischen den beiden Zylinder-Auslaß-Hubventilen 4 gleich dem in Richtung der Brennkraftmaschinen-Längsachse 2 gemesse- nen Abstand xe zwischen den beiden Zylinder-Einlaß-Hubventilen 3. Demzufolge ist es möglich, die Aktuatoren 14 der Auslaß-Hubventiie 4 sowie die Aktuatoren 13 der Einlaß-Hubventile 3 derart auszubilden, daß die Aktuatoren 13 und 14 ein im wesentlichen gleiches Längsmaß L (in Richtung der Brennkraftmaschinen-Längsachse 2 gemessen) besitzen. Wie besonders deutlich aus Fig.1 aber auch aus Fig.2 hervorgeht, ist das Breitenmaß B der den Einlaß-Hubventilen 3 zugeordneten Aktuatoren 13 jedoch geringer als das Breitenmaß B der den Auslaß-Hubventilen 4 zugeordneten Aktuatoren 14. Demzufolge ist die Querschnittsfläche 13b der Ak- tuatoren 13 geringer als die Querschnittsfläche 14b der Aktuatoren 14.As FIG. 2 shows, 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 measured in the direction of the longitudinal axis 2 of the internal combustion engine 3. 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) . As can be seen particularly clearly from FIG. 1 but also from FIG. 2, the width dimension B of the actuators 13 assigned to the inlet lift valves 3 is, however, 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.
Wie vor Beginn der Figurenbeschreibung dieses bevorzugten Ausführungsbeispieles bereits ausführlicher erläutert wurde, kann die Querschnittsfläche 13b der sog. Einlaß-Aktuatoren 13 geringer sein als diejenige der sog. Aus- laß-Aktuatoren 14, nachdem die von den erstgenannten im Verlauf einer Öffnungsbewegung der Einlaß-Hubventile 4 zu erbringende Arbeit bzw. Leistung geringer ist als die von den letztgenannten im Verlauf einer Öffnungsbewegung der Auslaß-Hubventiie 4 zu erbringende Arbeit bzw. Leistung. Zwar wird mit dieser Maßnahme von einem grundsätzlich gewünschten Gleichteilekonzept abgewichen, d.h. die Auslaß-Aktuatoren 14 unterscheiden sich von den Einlaß-Aktuatoren 13, jedoch werden andererseits mit dieser Maßnahme signifikante Vorteile hinsichtlich des benötigten Bauraumes erzielt.As was already explained in more detail before the description of the figures of this preferred exemplary embodiment began, the cross-sectional area 13b of the so-called inlet actuators 13 can be smaller than that of the so-called outlet actuators 14 after the one of the former mentioned in the course of an opening movement of the inlet Lift valves 4 work or power to be performed is less than the work or power to be performed by the latter in the course of an opening movement of the outlet lift valve 4. This measure deviates from a principle of the same parts concept, i.e. The outlet actuators 14 differ from the inlet actuators 13, but on the other hand significant advantages are achieved with this measure in terms of the space required.
Diese Vorteile liegen klar auf der Hand und bedürfen eigentlich keiner weiteren Erläuterung. Wesentlich ist, daß die den jeweiligen Hubventilen 3 bzw. 4 zugeordneten elektromagnetischen Aktuatoren 13 bzw. 14 jeweils im Hinblick auf die von ihnen zu erbringende Arbeit dimensioniert und insbesondere auch hinsichtlich ihrer äußeren geometrischen Abmessungen, d.h. hier hinsichtlich ihrer Querschnittsflächen 13b bzw. 14b dimensioniert werden. Wird nun - wie oben sowie eingangs erläutert - für die eine kleinere Querschnittsfläche 13b und insbesondere ein kleineres Breitenmaß B aufweisenden Einlaß-Aktuatoren 13 ein geringerer Bauraum benötigt als für die demgegenüber größeren bzw. breiteren Auslaß-Aktuatoren 14, so kann dieser Gewinn von Bauraum anderweitig genutzt werden bzw. der gesamte von der Brennkraftmaschine als Ganzes benötigte Bauraum kann entsprechend reduziert werden.These advantages are obvious and do not really require any further explanation. It is essential that the electromagnetic actuators 13 and 14 assigned to the respective lift valves 3 and 4 are dimensioned in each case with regard to the work to be performed by them and in particular also with regard to their external geometric dimensions, ie here with regard to their cross-sectional areas 13b and 14b . If - as explained above and at the beginning - a smaller installation space is required for the inlet actuators 13, which have a smaller cross-sectional area 13b and in particular a smaller width dimension B, than for the larger or wider outlet actuators 14, on the other hand, this gain in installation space can otherwise be used or the whole of the Internal space as a whole, the installation space required can be reduced accordingly.
In diesem Sinne ist auch eine weitere Maßnahme zu sehen, die am bevor- zugten und in den Figuren 1, 2 dargestellten Ausführungsbeispiel realisiert ist. Ein zwischen der in Richtung der Brennkraftmaschinen-Längsachse 2 verlaufenden Ebene sämtlicher Auslaß-Hubventiie 4 sowie der dementspre- chenden Ebene sämtlicher Einlaß-Hubventile 3 vorgesehener Zündkerzendom 6 zur Aufnahme einer figürlich nicht dargestellten Zündkerze ist nämlich mit seiner Längsachse 6a zumindest geringfügig zu den Einlaß-Aktuatoren 13 hin geneigt, wobei der Schnittpunkt dieser Längsachse mit dem nicht dargestellten Zylinder-Brennraum im wesentlichen im Zentrum des Brennraumes liegt. Dabei weist selbstverständlich jeder Zylinder der mehrzylindri- gen Brennkraftmaschine einen derartigen Zündkerzendom 6 auf, wenngleich ein solcher in Fig.2 nur für den ersten (rechtsseitig liegenden) Zylinder dargestellt ist. Die mit der Längsachse der nicht dargestellten, montierten Zündkerze zur Deckung kommende Längsachse 6a des Zündkerzendomes 6 ist somit gegenüber der Hochachse 5 der Brennkraftmaschine geringfügig zu den Einlaß-Aktuatoren 13 hin geneigt, wie insbesondere aus Fig.1 hervor- geht. Dabei ist dieser Zündkerzendom 6 in Richtung der Brennkraftmaschinen-Längsachse 2 betrachtet im wesentlichen zwischen den beiden Einlaß- Hubventilen 3 (sowie zwischen den beiden Auslaß-Hubventilen 4) jedes Brennkraftmaschinen-Zylinders angeordnet. Daß auch diese Maßnahme zu einer Verringerung der gesamten Breite der Brennkraftmaschine (in Fig.2 senkrecht zur Längsachse 2 und in Fig.1 senkrecht zur Hochachse 5 gemessen) führt, liegt auf der Hand.In this sense, a further measure can also be seen, which is implemented on the preferred exemplary embodiment shown in FIGS. 1, 2. 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 intake Actuators 13 inclined, the intersection of this longitudinal axis with the cylinder combustion chamber, not shown, is essentially in the center of the combustion chamber. Here, of course, each cylinder of the multi-cylinder internal combustion engine has such a spark plug dome 6, although one is shown in FIG. 2 only for the first (right-hand) cylinder. The longitudinal axis 6a of the spark plug dome 6 which coincides with the longitudinal axis of the assembled spark plug (not shown) 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).
Mit der beschriebenen kompakten und raumsparenden Anordnung im Zylinderkopf 1 der Brennkraftmaschine, welche grundsätzlich äußerst vorteilhaft ist, kann es jedoch erforderlich sein, für eine ausreichende Kühlung der Ak- tuatoren 13, 14 zu sorgen, die selbstverständlich im Betrieb eine erhebliche Menge von Abwärme erzeugen. Eine reine Luftkühlung der elektromagnetischen Aktuatoren 13, 14 dürfte in den wenigsten Fällen ausreichend sein, weshalb hier unterstützende Maßnahmen vorgesehen sind. Diese Maßnah- men bestehen darin, daß im wesentlichen in Richtung der Brennkraftmaschinen-Längsachse 2 im Zylinderkopf 1 verlaufende Druckölkanäle 7 nahe der Unterseite 13a bzw. 14a der Aktuatoren 13 bzw. 14, mit welcher diese auf dem Zylinderkopf 1 aufliegen, vorgesehen sind. Die in den Aktuatoren 13, 14 anfallende Wärmemenge wird somit größtenteils über deren Unterseite 13a bzw. 14a an den Zylinderkopf 1 abgegeben und in diesem über das in den Druckölkanälen 7 geführte Schmieröl der Brennkraftmaschine abgeführt. Dabei kann ein Teil dieses in den Druckölkanälen 7 geführten Schmieröles auch durch die elektromagnetischen Aktuatoren 13, 14 hindurch geführt werden, und zwar nicht nur zu Schmierzwecken, sondern auch zu einer ver- stärkten Kühlung derselben (figürlich nicht dargestellt).With the described compact and space-saving arrangement in the cylinder head 1 of the internal combustion engine, which is fundamentally extremely advantageous, it may be necessary, however, to adequately cool the batteries. tuators 13, 14 to worry, which of course generate a significant amount of waste heat in operation. Pure air cooling of the electromagnetic actuators 13, 14 should be sufficient in the rarest of cases, which is why supporting measures are provided here. These measures consist in the fact that pressure oil channels 7 running in the cylinder head 1 essentially in the direction of the longitudinal axis 2 of the internal combustion engine are provided near the underside 13a and 14a of the actuators 13 and 14 with which they rest on the cylinder head 1. The amount of heat generated in the actuators 13, 14 is thus largely discharged to the cylinder head 1 via the underside 13a or 14a thereof and discharged into the cylinder head 1 via the lubricating oil of the internal combustion engine guided in the pressure oil channels 7. Part of this lubricating oil, which is guided in the pressure oil channels 7, can also be passed through the electromagnetic actuators 13, 14, not only for lubrication purposes, but also for increased cooling thereof (not shown in the figure).
Ebenfalls figürlich nicht dargestellt sind weitere Maßnahmen zur verstärkten Kühlung der Aktuatoren, die noch kurz erwähnt werden. So kann nahe der Unterseite 13a bzw. 14a der Aktuatoren 13 bzw. 14, mit welcher diese auf dem Zylinderkopf 1 aufliegen, eine relativ große Anhäufung von den Zylinderkopf 1 bildendem Material vorliegen, so daß dieses eine große Menge von an den Aktuatoren anfallender Abwärme aufnehmen kann. Weiterhin können nahe der Unterseite 13a bzw. 14a der Aktuatoren 13 bzw. 14, mit welcher diese auf dem Zylinderkopf 1 aufliegen, im Zylinderkopf 1 Kühlmittel- räume für ein den Zylinderkopf durchströmendes Kühlmittel vorgesehen sein. Daneben können selbstverständlich eine Vielzahl weiterer Details insbesondere konstruktiver Art durchaus abweichend vom gezeigten Ausführungsbeispiel gestaltet sein, ohne den Inhalt der Patentansprüche zu verlassen. Bezugszeichenliste:Further measures for increased cooling of the actuators, which are briefly mentioned, are also not shown in the figures. Thus, near the underside 13a or 14a of the actuators 13 or 14, with which they rest on the cylinder head 1, there can be a relatively large accumulation of material forming the cylinder head 1, so that these absorb a large amount of waste heat accumulating on the actuators can. Furthermore, near the underside 13a or 14a of the actuators 13 or 14 with which they rest on the cylinder head 1, coolant spaces for a coolant flowing through the cylinder head can be provided in the cylinder head 1. In addition, of course, a large number of further details, in particular of a constructive nature, can be designed quite differently from the exemplary embodiment shown, without departing from the content of the claims. Reference symbol list:
1 Zylinderkopf 1 a Boden von 11 cylinder head 1 a bottom of 1
2 Längsachse der Brennkraftmaschine2 longitudinal axis of the internal combustion engine
3 Einlaß-Hubventil3 Inlet lift valve
3' Achsrichtung von 33 'axis direction of 3
4 Auslaß-Hubventil 4' Achsrichtung von 44 outlet lift valve 4 'axial direction of 4
5 Hochachse der Brennkraftmaschine5 vertical axis of the internal combustion engine
6 Zündkerzendom 6' Längsachse von 66 spark plug dome 6 'longitudinal axis of 6
7 Druckölkanal 13 Aktuator für 3 (=Einlaß-Aktuator)7 pressure oil duct 13 actuator for 3 (= inlet actuator)
13a Unterseite von 1313a underside of 13
13b Querschnittsfläche von 1313b cross-sectional area of FIG. 13
14 Aktuator für 4 (=Auslaß-Aktuator)14 actuator for 4 (= outlet actuator)
14a Unterseite von 14 14b Querschnittsfläche von 1414a underside of 14 14b cross-sectional area of 14
B Breite / Breitenmaß von 13b bzw. 14bB Width / width dimension of 13b or 14b
L Länge / Längsmaß von 13b bzw. 14b xa Abstand zwischen den beiden Auslaß-Hubventilen 4 eines Zylinders xe Abstand zwischen den beiden Einlaß-Hubventilen 3 eines Zylinders L length / longitudinal dimension of 13b or 14b x a distance between the two exhaust lift valves 4 of a cylinder x e distance between the two intake lift valves 3 of a cylinder

Claims

Patentansprüche Patent claims
1 . Mehrzylindrige Breπnkraftmaschine mit von elektromagnetischen Aktuatoren (13, 14) betätigten und den Einlaß sowie den Auslaß der Zylinder-Brennräume steuernden Gaswechsel-Hubventilen (3, 4), dadurch gekennzeichnet, daß die senkrecht zur Achsrichtung (3', 4') der Hubventile (3, 4) liegende Querschnittsfläche (13b) der den Einlaß-Hubventilen (3) zugeordneten Aktuatoren (13) geringer ist als die dementsprechende Querschnittsfläche (14b) der den Auslaß- Hubventilen (4) zugeordneten Aktuatoren (14).1 . Multi-cylinder internal combustion engine with gas exchange lifting valves (3, 4) actuated by electromagnetic actuators (13, 14) and controlling the inlet and outlet of the cylinder combustion chambers, characterized in that the lifting valves (3', 4') are perpendicular to the axial direction (3', 4') 3, 4) lying cross-sectional area (13b) of the actuators (13) assigned to the inlet lift valves (3) is smaller than the corresponding cross-sectional area (14b) of the actuators (14) assigned to the outlet lift valves (4).
2. Brennkraftmaschine nach Anspruch 1 , wobei die Einlaß-Hubventile (3) sowie die Auslaß-Hubventiie (4) jeweils in Richtung der Brennkraftmaschinen-Längsachse (2) in Reihe hintereinander angeordnet sind, dadurch gekennzeichnet, daß die in der Ebene der Aktuator- Querschnittsflache (13b, 14b) sowie senkrecht zur Brennkraftmaschi- nen-Längsachse (2) gemessene Breite (B) der Einlaß-Aktuatoren (13) geringer ist als die dementsprechende Breite (B) der Auslaß- Aktuatoren (14).2. Internal combustion engine according to claim 1, wherein the inlet lifting valves (3) and the outlet lifting valves (4) are each arranged one behind the other in the direction of the longitudinal axis of the internal combustion engine (2), characterized in that in the plane of the actuator Cross-sectional area (13b, 14b) and width (B) of the inlet actuators (13) measured perpendicular to the longitudinal axis (2) of the internal combustion engine is less than the corresponding width (B) of the outlet actuators (14).
3. Brennkraftmaschine nach Anspruch 1 oder 2, mit jeweils zwei Einlaß- Hubventilen (3) und Auslaß-Hubventilen (4) je Zylinder, dadurch gekennzeichnet, daß der in Richtung der Brennkraftmaschinen-Längsachse (2) gemessene Abstand (xa) zwischen den beiden Zylinder-Auslaß-Hubventilen (4) gleich dem entsprechenden Abstand (xe) zwischen den beiden Zylinder-Einlaß-Hubventiien (3) ist. 3. Internal combustion engine according to claim 1 or 2, each with two inlet lift valves (3) and outlet lift valves (4) per cylinder, characterized in that the distance (x a ) measured in the direction of the internal combustion engine longitudinal axis (2) between the both cylinder outlet lifting valves (4) is equal to the corresponding distance (x e ) between the two cylinder inlet lifting valves (3).
. Brennkraftmaschine nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, daß ein zwischen der Ebene der Auslaß- Hubventile . Internal combustion engine according to one of the preceding claims, characterized in that a lift valve between the plane of the outlet
(4) sowie der Ebene der Einlaß-Hubventile (3) vorgesehe- ner Zündkerzendom (6) zur Aufnahme einer Zündkerze mit seiner(4) and the level of the inlet lift valves (3) provided spark plug dome (6) to accommodate a spark plug with its
Längsachse (6a) zumindest geringfügig zu den Einlaß-Aktuatoren (13) hin geneigt ist.Longitudinal axis (6a) is at least slightly inclined towards the inlet actuators (13).
5. Brennkraftmaschine nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, daß im wesentlichen in Richtung der Brennkraftmaschinen-Längsachse (2) im Brennkraftmaschinen-Zylinderkopf (1) verlaufende Druckölkanäle (7) nahe der Unterseite (13a, 14a) der Aktuatoren (13, 14), mit welcher diese auf dem Zylinderkopf (1) aufliegen, vorgesehen sind.5. Internal combustion engine according to one of the preceding claims, characterized in that pressure oil channels (7) running essentially in the direction of the internal combustion engine longitudinal axis (2) in the internal combustion engine cylinder head (1) near the underside (13a, 14a) of the actuators (13, 14 ), with which they rest on the cylinder head (1), are provided.
6. Brennkraftmaschine nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, daß nahe der Unterseite (13a, 14a) der Aktuatoren (13, 14), mit welcher diese auf dem Zylinderkopf (1 ) aufliegen, eine relativ große Anhäufung von den Zylinderkopf (1 ) bildendem Material vorliegt.6. Internal combustion engine according to one of the preceding claims, characterized in that near the underside (13a, 14a) of the actuators (13, 14), with which they rest on the cylinder head (1), there is a relatively large accumulation of the cylinder head (1) forming material is present.
7. Brennkraftmaschine nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, daß nahe der Unterseite (13a, 14a) der Aktuatoren (13, 14), mit welcher diese auf dem Zylinderkopf (1 ) auflie- gen, im Zylinderkopf (1 ) Kühlmittelräume für ein den Zylinderkopf (1 ) durchströmendes Kühlmittel vorgesehen sind. 7. Internal combustion engine according to one of the preceding claims, characterized in that near the underside (13a, 14a) of the actuators (13, 14), with which they rest on the cylinder head (1), there are coolant spaces in the cylinder head (1) for a Coolant flowing through the cylinder head (1) is provided.
EP00904881A 1999-02-24 2000-01-07 Multicylinder internal combustion engine with gas flow lift valves actuated by electromagnetic actuators Expired - Lifetime EP1155223B1 (en)

Applications Claiming Priority (3)

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DE19907850 1999-02-24
DE19907850A DE19907850C2 (en) 1999-02-24 1999-02-24 Multi-cylinder internal combustion engine with gas exchange lift valves actuated by electromagnetic actuators
PCT/EP2000/000064 WO2000050741A1 (en) 1999-02-24 2000-01-07 Multicylinder internal combustion engine with gas flow lift valves actuated by electromagnetic actuators

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US6568358B1 (en) 2003-05-27
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