EP0736133B1 - Multi-cylinder internal-combustion engine - Google Patents

Multi-cylinder internal-combustion engine Download PDF

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Publication number
EP0736133B1
EP0736133B1 EP95903790A EP95903790A EP0736133B1 EP 0736133 B1 EP0736133 B1 EP 0736133B1 EP 95903790 A EP95903790 A EP 95903790A EP 95903790 A EP95903790 A EP 95903790A EP 0736133 B1 EP0736133 B1 EP 0736133B1
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EP
European Patent Office
Prior art keywords
exhaust
cylinders
row
cylinder
inlet
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Expired - Lifetime
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EP95903790A
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German (de)
French (fr)
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EP0736133A1 (en
Inventor
Klaus Fuoss
Wilhelm Hannibal
Michael Paul
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Audi AG
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Audi AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/221—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinder banks in narrow V-arrangement, having a single cylinder head
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/265—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder peculiar to machines or engines with three or more intake valves per cylinder
    • 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
    • F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings

Definitions

  • the invention relates to a multi-cylinder internal combustion engine according to the preamble of claim 1.
  • the invention has for its object an internal combustion engine to create the generic type, in which the Combustion chambers and the intake and exhaust channels of all cylinders can also be formed identically, in which but cylinder-selective fuel injection is no problem provided and the heating of the aspirated mixture can be kept low, more than two Intake valves can be provided per cylinder and finally, an optimal guidance of the outlet channels is realized is.
  • each inlet duct an injection valve with spray direction on the or to provide associated intake valves. Because the Inlet channels are on the outside, heating of the intake Mixtures avoided or at least reduced. Due to the external arrangement of the inlet valve rows there is also the possibility of taking up little space to provide long intake ports, reducing torque is increased in the lower speed range. Finally, you can in that each intake camshaft only the intake valves actuated in a row of cylinders on each intake camshaft more than two cams can be accommodated per cylinder, so that easily with an internal combustion engine, for example three intake valves per cylinder can be realized.
  • the drive element is with connected to the exhaust camshaft and the output element is preferably over one with both intake camshafts Chain gear connected, the output element of the Adjustment device and the intake camshafts sprockets have the same diameter.
  • the diameter of this Sprockets can be significantly smaller than that on the Exhaust camshaft seated, with the crankshaft in drive connection stationary drive wheel, with which the width of the cylinder head, which depends largely on the diameter of the sprockets seated on the intake camshafts is reduced. Naturally, this is particularly important when installing such an internal combustion engine in the engine compartment of a motor vehicle.
  • the cylinders are arranged in two rows, the cylinders 1 of the one row to the cylinders 2 of the other row stand on a gap and the longitudinal central axes the cylinder of one row with the longitudinal central axes the cylinder of the other row makes an angle include, as can be seen from Fig. 2.
  • the cylinder head 3 contains 1 of the first for each cylinder Row of cylinders three intake ports 4 by a common intake port 5 go out and open into inlet openings 6, which are dominated by inlet valves 7. Each cylinder 1 the first row of cylinders are also two exhaust ports 8 assigned, which combined into a collective outlet channel 9 are and start from outlet openings 10, which of Exhaust valves 11 are controlled. In a similar way are three for cylinders 2 of the second cylinder bank Inlet channels 4 'are provided, which open into inlet openings 6', which are controlled by inlet valves 7 ', and two outlet channels 8 ', which start from outlet openings 10', which are controlled by exhaust valves 11 '.
  • the exhaust valves 11, 11 'of all cylinders 1, 2 are each in two extending in the longitudinal direction of the machine Exhaust valve rows A and B arranged, which to both Sides and close to that between the rows of cylinders Plane of symmetry S lie.
  • the exhaust valves 11, 11 ' Both cylinder rows are over the tappet 12 from the Actuated cam 13 of a common exhaust camshaft 14, which lies in said plane of symmetry S.
  • the intake valves 7, 7 'of the two rows of cylinders are arranged on the outside and are each created by the cams of their own, external intake camshaft 15 and 15 'actuated.
  • the Exhaust camshaft 14 carries a drive wheel 16, which with the Crankshaft in drive connection.
  • This known adjustment device is shown in detail in Fig. 3 and has a sleeve-shaped Drive element 18 on that with the drive wheel 16 in one piece and with the exhaust camshaft 14 rotatably connected is.
  • the adjusting device 17 also has an output element 19 on the inside of the drive element 18 rotatably mounted on the exhaust camshaft 14 is and carries an output gear 20, which by a Chain 21 with arranged on the intake camshafts 15, 15 ' Sprockets 22, 22 'are in drive connection.
  • the drive element 18 has an internal longitudinal toothing 23 and the output element 19 is with an outer Provide helical teeth 24. Between the drive element 18 and the output element 19 is an annular adjusting piston 25 arranged, the one with the toothing 23rd engaging spur gear 26 and one with the Gearing 24 helical gearing 27 engaged having. As a result, the drive element 18 is rotatably fixed connected to the output element 19. By moving the Adjusting piston 25 can be the angular position of the output element 19 compared to the drive element 18 and thus the Angular position of the intake camshafts 15, 15 'opposite the exhaust camshaft 14 can be changed. The adjustment of the adjusting piston 25 takes place against the force of one Spring 28 by pressurizing the left face of the adjusting piston 27. Such an adjusting device is described for example in DE-A 29 09 803.
  • the inlet valves 7, 7 ' are in the embodiment Rocker arm operated, with variable valve timing is provided with which a different actuation in a lower and an upper speed range can.
  • a variable valve control is described for example in DE-A 42 05 230.
  • a first cam 30 intended for the lower speed range, which with a first rocker arm 31 cooperates, which on the corresponding Inlet valve 7 or 7 'acts.
  • the first rocker arms 31 can be used with the second rocker arms 33 are coupled by coupling bolts 34, whereby then the intake valves according to the contour of the second cam 32 are actuated.
  • All first and second Rocker arms 31, 33 for the intake valves of a row of cylinders are mounted on a common axis 35, the contains a channel 36 through which a pressure medium is supplied can be that the coupling pin 34 against the Force a spring 37 in the clutch position.
  • the inlet manifolds extend 5 outwards and upwards to the top 37 of the Cylinder head.
  • Each inlet manifold 5 is an injection valve 38 assigned that towards the three Inlet valves 7 and 7 'injected.
  • On the top 37 of the A cylinder head cover 39 is placed on the cylinder head 3.
  • the inlet manifolds 5 sit in channels 40 in the Cylinder head cover 39 continues with a not shown Intake manifold are connected.
  • the sprockets 20 and 22, 22 ' have the same diameter. This diameter can be smaller than the diameter of the exhaust camshaft drive wheel 16. This can Overall width of the cylinder head 3 in the area of the camshaft drive, which depend largely on the diameter of the gears 22, 22 'is determined to be kept relatively small.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The invention concerns a multi-cylinder internal-combustion engine in which the cylinders (1, 2) are disposed in two rows, the cylinders (1) in one row being staggered with respect to the cylinders (2) in the other row and the longitudinal axes of the cylinders in the first row being disposed at an angle to the longitudinal axes of the cylinders in the other row. The outlet valves (11, 11') are located close to the plane of symmetry (S) between the rows of cylinders whereas the inlet valves (7, 7') are located out of this plane. Provided for all the outlet valves of both rows of cylinders is a common centrally located camshaft (14) and provided for the inlet valves of each row of cylinders are dedicated side-located camshafts (15 and 15', respectively).

Description

Die Erfindung betrifft eine Mehrzylinder-Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a multi-cylinder internal combustion engine according to the preamble of claim 1.

Bei einer bekannten Brennkraftmaschine dieser Art (DE-A 32 43 013) wechseln sich die Einlaß- und Auslaßventilreihen ab, d. h. quer zur Längsrichtung der Maschine folgt auf einer Auslaßventilreihe eine Einlaßventilreihe, dann wieder eine Auslaßventilreihe und schließlich noch eine Einlaßventilreihe. Es sind zwei Nockenwellen, eine Einlaßnockenwelle und eine Auslaßnockenwelle, vorgesehen, die über den äußeren Ventilreihen liegen und jeweils die Ventile der äußeren Ventilreihe und die Ventile der nicht benachbarten inneren Ventilreihe betätigen. Die Ventile der inneren Ventilreihen sind dabei zwangsläufig stark gegenüber den Längsmittelachsen der zugehörigen Zylinder geneigt, wodurch sich eine ungünstige Brennraumform ergibt. Da außerdem die Länge der Einlaß- und Auslaßkanäle der beiden Zylinderreihen unterschiedlich ist, ist nicht sichergestellt, daß in allen Zylindern die gleiche Füllungs- und Verbrennungsverhältnisse vorliegen.In a known internal combustion engine of this type (DE-A 32 43 013) the inlet and outlet valve rows alternate from, d. H. transverse to the longitudinal direction of the machine follows an exhaust valve row, an intake valve row, then again an exhaust valve row and finally an intake valve row. There are two camshafts, one intake camshaft and an exhaust camshaft provided the valves are above the outer rows of valves the outer row of valves and the valves of the non-adjacent ones Actuate inner row of valves. The valves of the inner rows of valves are inevitably strongly opposite inclined to the longitudinal central axes of the associated cylinders, which results in an unfavorable combustion chamber shape. In addition, since the length of the inlet and outlet channels two rows of cylinders is different is not guaranteed that the same filling in all cylinders and combustion conditions exist.

Um diese Nachteile zu vermeiden, ist es bekannt (DE-A 38 31 333), die Einlaßventilreihen zu beiden Seiten und nahe der zwischen den Zylinderreihen verlaufenden Symmetrieebene, die Auslaßventilreihen jedoch außen anzuordnen und für die beiden Einlaßventilreihen eine gemeinsame Einlaßnokkenwelle in der genannten Symmetrieebene und für jede Auslaßventilreihe eine eigene Auslaßnockenwelle vorzusehen. To avoid these disadvantages, it is known (DE-A 38 31 333), the inlet valve rows on both sides and close the plane of symmetry between the rows of cylinders, the rows of exhaust valves, however, to be arranged outside and for the two intake valve rows share a common intake camshaft in the named plane of symmetry and for each exhaust valve row to provide its own exhaust camshaft.

Dadurch wird für alle Zylinder eine identische Ausbildung der Brennräume sowie der Einlaß- und Auslaßkanäle ermöglicht, womit eine gleichmäßige Füllung und ein identischer Verbrennungsablauf für alle Zylinder gewährleistet ist. Es hat sich jedoch gezeigt, daß bei dieser Brennkraftmaschine eine zylinderselektive Kraftstoffeinspritzung, die für eine gute Gemischaufbereitung wesentlich ist, praktisch nicht verwirklicht werden kann. Außerdem ist aufgrund der innenliegenden Einlaßkanäle eine starke Erwärmung des angesaugten Gemisches und der dadurch bedingte Füllungsverlust unvermeidlich. Schließlich ist diese Konstruktion für eine Brennkraftmaschine mit mehr als zwei Einlaßventile pro Zylinder nicht brauchbar, da auf der allen Einlaßventilen gemeinsamen Einlaßnockenwelle kein Platz für mehr als zwei Nocken pro Zylinder vorhanden ist. Aufgrund dieser beengten Platzverhältnisse ist auch eine Betätigung der Einlaßventile nur über Tassenstößel, nicht jedoch über Schwinghebel möglich.This creates an identical training for all cylinders the combustion chambers as well as the inlet and outlet channels, with an even filling and an identical one Combustion process is guaranteed for all cylinders. It However, it has been shown that in this internal combustion engine a cylinder selective fuel injection, which for good mixture preparation is essential, practical cannot be realized. In addition, due to the internal intake ducts cause excessive warming of the intake Mixture and the resulting loss of filling inevitable. After all, this construction is for an internal combustion engine with more than two intake valves not usable per cylinder, because on all intake valves common intake camshaft no more room for than two cams per cylinder. Based on these cramped space is also an operation of the inlet valves only via tappets, but not via Rocker arm possible.

Der Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine der gattungsgemäßen Art zu schaffen, bei der die Brennräume und die Einlaß- und Auslaßkanäle aller Zylinder ebenfalls identisch ausgebildet werden können, bei der aber eine zylinderselektive Kraftstoffeinspritzung problemlos vorgesehen und die Erwärmung des angesaugten Gemisches gering gehalten werden kann, mehr als zwei Einlaßventile pro Zylinder vorgesehen werden können und schließlich eine optimale Führung der Auslaßkanäle realisiert ist.The invention has for its object an internal combustion engine to create the generic type, in which the Combustion chambers and the intake and exhaust channels of all cylinders can also be formed identically, in which but cylinder-selective fuel injection is no problem provided and the heating of the aspirated mixture can be kept low, more than two Intake valves can be provided per cylinder and finally, an optimal guidance of the outlet channels is realized is.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst.This object is achieved by the features of Claim 1 solved.

Dadurch, daß bei dem erfindungsgemäßen Vorschlag die Einlaßventilreihen außen angeordnet sind, können die Einlaßkanäle schräg von außen nach innen verlaufend vorgesehen werden.Characterized in that the inlet valve rows in the proposal according to the invention are arranged outside, the inlet channels provided inclined from the outside inwards will.

Damit ergibt sich die Möglichkeit, in jedem Einlaßkanal ein Einspritzventil mit Spritzrichtung auf das oder die zugehörigen Einlaßventile vorzusehen. Dadurch, daß die Einlaßkanäle außen liegen, wird eine Aufheizung des angesaugten Gemisches vermieden oder jedenfalls verringert. Durch die außenliegende Anordnung der Einlaßventilreihen ergibt sich zudem die Möglichkeit, bei geringem Platzbedarf lange Einlaßkanäle vorzusehen, wodurch das Drehmoment im unteren Drehzahlbereich erhöht wird. Schließlich können dadurch, daß jede Einlaßnockenwelle nur die Einlaßventile einer Zylinderreihe betätigt, auf jeder Einlaßnockenwelle mehr als zwei Nocken pro Zylinder untergebracht werden, so daß problemlos eine Brennkraftmaschine mit beispielsweise drei Einlaßventilen pro Zylinder verwirklicht werden kann. Auch ist bei der vorgeschlagenen Anordnung der Einlaßnokkenwellen genug Platz vorhanden, um die Einlaßventile auch über Schlepp- oder Kipphebel betätigen zu können, was insbesondere deshalb von Bedeutung ist, weil dadurch die Möglichkeit besteht, eine variable Ventilsteuerung beispielsweise entsprechend der DE-A 42 05 230 unterzubringen. Der erfindungsgemäße Vorschlag bietet auch die Möglichkeit, ohne wesentliche Änderung des Zylinderkopfes eine Brennkraftmaschine wahlweise mit Tassenstößel-Steuerung oder mit Schlepp- oder Kipphebelsteuerung für Einlaßventile zu verwirklichen. Darüber hinaus wird dadurch, daß die Auslaßkanäle der Zylinder einer jeden Zylinderreihe sich von den jeweiligen brennraumseitigen Auslaßöffnungen über die jeweils benachbarte Zylinderreihe hinweg zur jeweiligen Zylinderkopfseite erstrecken, erreicht, daß die Abgasleitungen relativ geradlinig nach außen weggeführt werden können. Hierdurch ergibt sich eine nur minimale Verlängerung der Abgasleitungen und werden zusätzliche Krümmungen derselben vermieden.This creates the possibility in each inlet duct an injection valve with spray direction on the or to provide associated intake valves. Because the Inlet channels are on the outside, heating of the intake Mixtures avoided or at least reduced. Due to the external arrangement of the inlet valve rows there is also the possibility of taking up little space to provide long intake ports, reducing torque is increased in the lower speed range. Finally, you can in that each intake camshaft only the intake valves actuated in a row of cylinders on each intake camshaft more than two cams can be accommodated per cylinder, so that easily with an internal combustion engine, for example three intake valves per cylinder can be realized. Also in the proposed arrangement of the inlet camshafts enough space to hold the intake valves too to be able to operate via rocker arm or rocker arm, which in particular is important because it gives the opportunity there is a variable valve control, for example to accommodate according to DE-A 42 05 230. Of the proposal according to the invention also offers the possibility of an internal combustion engine without significant change to the cylinder head either with tappet control or with rocker or rocker arm control for intake valves too realize. In addition, the fact that Exhaust ports of the cylinders of each row of cylinders themselves from the respective outlet openings on the combustion chamber the respective neighboring row of cylinders to extend each cylinder head side, achieved that the Exhaust pipes are led away to the outside in a relatively straight line can be. This results in only a minimal one Extend the exhaust pipes and become additional Avoid curvatures of the same.

Vorteilhaft sind bei zwei Auslaßventilen je Zylinder die zwei Auslaßkanäle jeweils zu einem Sammelauslaßkanal zusammengefaßt. Auf diese Weise kann der erforderliche Platzbedarf der Abgasleitung reduziert werden.Are advantageous with two exhaust valves per cylinder two outlet channels each to a collective outlet channel summarized. In this way, the required Space requirements of the exhaust pipe can be reduced.

Um eine hohe Leistung und ein hohes Drehmoment über den gesamten Drehzahlbereich zu erreichen, ist es bekannt, die Einlaßnockenwellen drehzahlabhängig gegenüber der antreibenden Kurbelwelle zu verdrehen, um in allen Drehzahlbereichen optimale Füllungsverhältnisse zu erreichen. Während bisher zu diesem Zweck auf jeder Einlaßnockenwelle eine eigene Verstelleinrichtung vorgesehen wurde, wird gemäß einem weiteren Vorschlag der Erfindung nur eine einzige Verstelleinrichtung für beide Einlaßnockenwellen vorgesehen, und zwar vorzugsweise auf der Auslaßnockenwelle, die dann als einzige Nockenwelle direkt von der Kurbelwelle angetrieben wird. Nockenwellen-Verstelleinrichtungen weisen in aller Regel ein von der Kurbelwelle angetriebenes Antriebselement und ein gegenüber diesem verdrehbares Abtriebselement auf. Folglich ist das Antriebselement mit der Auslaßnockenwelle verbunden und das Abtriebselement ist mit beiden Einlaßnockenwellen vorzugsweise über ein Kettengetriebe verbunden, wobei das Abtriebselement der Verstelleinrichtung und die Einlaßnockenwellen Kettenräder gleichen Durchmessers aufweisen. Der Durchmesser dieser Kettenräder kann erheblich kleiner sein als das auf der Auslaßnockenwelle sitzende, mit der Kurbelwelle in Antriebsverbindung stehende Antriebsrad, womit die Baubreite des zylinderkopfes, die maßgeblich von dem Durchmesser der auf den Einlaßnockenwellen sitzenden Kettenrädern bestimmt ist, verringert ist. Dies hat naturgemäß besondere Bedeutung beim Einbau einer derartigen Brennkraftmaschine in den Motorraum eines Kraftfahrzeuges.To achieve high performance and high torque over the To reach the entire speed range, it is known that Intake camshafts depending on the speed compared to the driving Crankshaft to twist in all speed ranges to achieve optimal filling ratios. While so far for this purpose on every intake camshaft a separate adjustment device has been provided in accordance with another proposal of the invention only one Adjustment device provided for both intake camshafts, preferably on the exhaust camshaft, which is then the only camshaft directly from the crankshaft is driven. Camshaft adjusters usually have a driven by the crankshaft Drive element and a rotatable relative to this Output element on. Consequently, the drive element is with connected to the exhaust camshaft and the output element is preferably over one with both intake camshafts Chain gear connected, the output element of the Adjustment device and the intake camshafts sprockets have the same diameter. The diameter of this Sprockets can be significantly smaller than that on the Exhaust camshaft seated, with the crankshaft in drive connection stationary drive wheel, with which the width of the cylinder head, which depends largely on the diameter of the sprockets seated on the intake camshafts is reduced. Naturally, this is particularly important when installing such an internal combustion engine in the engine compartment of a motor vehicle.

Ein Ausführungsbeispiel der Erfindung wird im folgenden unter Bezugnahme auf die Zeichnungen beschrieben. Es zeigt:

Fig. 1:
eine Draufsicht eines Abschnittes eines Zylinderkopfs, einer Mehrzylinder-Brennkraftmaschine mit teilweise weggebrochener Zylinderkopfhaube,
Fig. 2:
einen Schnitt entlang Linie 2-2 in Fig. 1, und
Fig. 3:
das vordere Ende der Auslaßnockenwelle mit der Verstelleinrichtung für die Einlaßnockenwellen, teilweise geschnitten.
An embodiment of the invention is described below with reference to the drawings. It shows:
Fig. 1:
1 shows a plan view of a section of a cylinder head, a multi-cylinder internal combustion engine with a partially broken off cylinder head cover,
Fig. 2:
a section along line 2-2 in Fig. 1, and
Fig. 3:
partially cut the front end of the exhaust camshaft with the adjusting device for the intake camshafts.

Bei der in den Zeichnungen dargestellten Mehrzylinder-Brennkraftmaschine sind die Zylinder in zwei Reihen angeordnet, wobei die Zylinder 1 der einen Reihe zu den Zylindern 2 der anderen Reihe auf Lücke stehen und die Längsmittelachsen der Zylinder der einen Reihe mit den Längsmittelachsen der Zylinder der anderen Reihe einen Winkel einschließen, wie dies aus Fig. 2 ersichtlich ist.In the multi-cylinder internal combustion engine shown in the drawings the cylinders are arranged in two rows, the cylinders 1 of the one row to the cylinders 2 of the other row stand on a gap and the longitudinal central axes the cylinder of one row with the longitudinal central axes the cylinder of the other row makes an angle include, as can be seen from Fig. 2.

Der Zylinderkopf 3 enthält für jeden Zylinder 1 der ersten Zylinderreihe drei Einlaßkanäle 4, die von einem Sammeleinlaßkanal 5 ausgehen und in Einlaßöffnungen 6 münden, die von Einlaßventilen 7 beherrscht sind. Jedem Zylinder 1 der ersten zylinderreihe sind außerdem zwei Auslaßkanäle 8 zugeordnet, die zu einem Sammelauslaßkanal 9 zusammengefaßt sind und von Auslaßöffnungen 10 ausgehen, welche von Auslaßventilen 11 beherrscht sind. In entsprechender Weise sind für die Zylinder 2 der zweiten Zylinderreihe drei Einlaßkanäle 4' vorgesehen, die in Einlaßöffnungen 6' münden, welche von Einlaßventilen 7' beherrscht sind, sowie zwei Auslaßkanäle 8', die von Auslaßöffnungen 10' ausgehen, welche von Auslaßventilen 11' beherrscht sind.The cylinder head 3 contains 1 of the first for each cylinder Row of cylinders three intake ports 4 by a common intake port 5 go out and open into inlet openings 6, which are dominated by inlet valves 7. Each cylinder 1 the first row of cylinders are also two exhaust ports 8 assigned, which combined into a collective outlet channel 9 are and start from outlet openings 10, which of Exhaust valves 11 are controlled. In a similar way are three for cylinders 2 of the second cylinder bank Inlet channels 4 'are provided, which open into inlet openings 6', which are controlled by inlet valves 7 ', and two outlet channels 8 ', which start from outlet openings 10', which are controlled by exhaust valves 11 '.

Die Auslaßventile 11, 11' aller Zylinder 1, 2 sind jeweils in zwei sich in Längsrichtung der Maschine erstreckenden Auslaßventilreihen A und B angeordnet, welche zu beiden Seiten und nahe der zwischen den Zylinderreihen verlaufenden Symmetrieebene S liegen. Die Auslaßventile 11, 11' beider Zylinderreihen werden über Tassenstößel 12 von den Nocken 13 einer gemeinsamen Auslaßnockenwelle 14 betätigt, die in der genannten Symmetrieebene S liegt. Die Einlaßventile 7, 7' der beiden Zylinderreihen sind außen angeordnet und werden jeweils von den Nocken einer eigenen, außenliegenden Einlaßnockenwelle 15 bzw. 15' betätigt. Die Auslaßnockenwelle 14 trägt ein Antriebsrad 16, das mit der Kurbelwelle in Antriebsverbindung steht. The exhaust valves 11, 11 'of all cylinders 1, 2 are each in two extending in the longitudinal direction of the machine Exhaust valve rows A and B arranged, which to both Sides and close to that between the rows of cylinders Plane of symmetry S lie. The exhaust valves 11, 11 ' Both cylinder rows are over the tappet 12 from the Actuated cam 13 of a common exhaust camshaft 14, which lies in said plane of symmetry S. The intake valves 7, 7 'of the two rows of cylinders are arranged on the outside and are each created by the cams of their own, external intake camshaft 15 and 15 'actuated. The Exhaust camshaft 14 carries a drive wheel 16, which with the Crankshaft in drive connection.

Der Antrieb der Einlaßnockenwellen 15, 15' erfolgt im Ausführungsbeispiel von der Auslaßnockenwelle 14 aus, und zwar über eine Verstelleinrichtung 17, mit der die Winkelstellung der Einlaßnockenwellen gegenüber der Auslaßnokkenwelle und damit gegenüber der Kurbelwelle verändert werden kann. Diese an sich bekannte Verstelleinrichtung ist in Fig. 3 im einzelnen dargestellt und weist ein hülsenförmiges Antriebselement 18 auf, das mit dem Antriebsrad 16 einstückig und mit der Auslaßnockenwelle 14 drehfest verbunden ist. Die Verstelleinrichtung 17 weist ferner ein Abtriebselement 19 auf, das innerhalb des Antriebselements 18 drehbar auf der Auslaßnockenwelle 14 gelagert ist und ein Abtriebsrad 20 trägt, das durch eine Kette 21 mit auf den Einlaßnockenwellen 15, 15' angeordneten Kettenrädern 22, 22' in Antriebsverbindung steht. Das Antriebselement 18 ist mit einer inneren Längsverzahnung 23 und das Abtriebselement 19 ist mit einer äußeren Schrägverzahnung 24 versehen. Zwischen dem Antriebselement 18 und dem Abtriebselement 19 ist ein ringförmiger Verstellkolben 25 angeordnet, der eine mit der Verzahnung 23 in Eingriff stehende Geradverzahnung 26 und eine mit der Verzahnung 24 in Eingriff stehende Schrägverzahnung 27 aufweist. Dadurch ist das Antriebselement 18 drehfest mit dem Abtriebselement 19 verbunden. Durch Verschiebung des Verstellkolbens 25 kann die Winkelstellung des Abtriebselements 19 gegenüber dem Antriebselement 18 und damit die Winkelstellung der Einlaßnockenwellen 15, 15' gegenüber der Auslaßnockenwelle 14 verändert werden. Die Verstellung des Verstellkolbens 25 erfolgt entgegen der Kraft einer Feder 28 durch Druckbeaufschlagung der linken Stirnfläche des Verstellkolbens 27. Eine derartige Verstelleinrichtung ist beispielsweise in der DE-A 29 09 803 beschrieben. The inlet camshafts 15, 15 'are driven in the exemplary embodiment from the exhaust camshaft 14, and via an adjusting device 17 with which the angular position the intake camshafts versus the exhaust camshafts and thus changed compared to the crankshaft can be. This known adjustment device is shown in detail in Fig. 3 and has a sleeve-shaped Drive element 18 on that with the drive wheel 16 in one piece and with the exhaust camshaft 14 rotatably connected is. The adjusting device 17 also has an output element 19 on the inside of the drive element 18 rotatably mounted on the exhaust camshaft 14 is and carries an output gear 20, which by a Chain 21 with arranged on the intake camshafts 15, 15 ' Sprockets 22, 22 'are in drive connection. The drive element 18 has an internal longitudinal toothing 23 and the output element 19 is with an outer Provide helical teeth 24. Between the drive element 18 and the output element 19 is an annular adjusting piston 25 arranged, the one with the toothing 23rd engaging spur gear 26 and one with the Gearing 24 helical gearing 27 engaged having. As a result, the drive element 18 is rotatably fixed connected to the output element 19. By moving the Adjusting piston 25 can be the angular position of the output element 19 compared to the drive element 18 and thus the Angular position of the intake camshafts 15, 15 'opposite the exhaust camshaft 14 can be changed. The adjustment of the adjusting piston 25 takes place against the force of one Spring 28 by pressurizing the left face of the adjusting piston 27. Such an adjusting device is described for example in DE-A 29 09 803.

Die Einlaßventile 7, 7' werden im Ausführungsbeispiel über Schlepphebel betätigt, wobei eine variable Ventilsteuerung vorgesehen ist, mit welcher eine unterschiedliche Betätigung in einem unteren und einem oberen Drehzahlbereich erfolgen kann. Eine derartige variable Ventilsteuerung ist beispielsweise in der DE-A 42 05 230 beschrieben. Hierbei ist auf der Einlaßnockenwelle 15 bzw. 15' für jedes Einlaßventil 7 bzw. 7' eines Zylinders ein erster Nocken 30 für den unteren Drehzahlbereich vorgesehen, der mit einem ersten Schlepphebel 31 zusammenwirkt, welcher auf das entsprechende Einlaßventil 7 bzw. 7' wirkt. Zwischen benachbarten ersten Nocken 30 ist auf jede Einlaßnockenwelle ein zweiter Nocken 32 für den oberen Drehzahlbereich vorgesehen, der mit einem zweiten Schlepphebel 33 zusammenwirkt. Die ersten Schlepphebel 31 können mit den zweiten Schlepphebeln 33 durch Kupplungsbolzen 34 gekoppelt werden, wodurch dann die Einlaßventile entsprechend der Kontur der zweiten Nocken 32 betätigt werden. Alle ersten und zweiten Schlepphebel 31, 33 für die Einlaßventile einer Zylinderreihe sind auf einer gemeinsamen Achse 35 gelagert, die einen Kanal 36 enthält, durch den ein Druckmittel zugeführt werden kann, das die Kupplungsbolzen 34 entgegen der Kraft einer Feder 37 in die Kupplungsstellung bringt.The inlet valves 7, 7 'are in the embodiment Rocker arm operated, with variable valve timing is provided with which a different actuation in a lower and an upper speed range can. Such a variable valve control is described for example in DE-A 42 05 230. Here is on the intake camshaft 15 and 15 'for each intake valve 7 or 7 'of a cylinder, a first cam 30 intended for the lower speed range, which with a first rocker arm 31 cooperates, which on the corresponding Inlet valve 7 or 7 'acts. Between neighboring first cam 30 is on each intake camshaft second cam 32 is provided for the upper speed range, which interacts with a second rocker arm 33. The first rocker arms 31 can be used with the second rocker arms 33 are coupled by coupling bolts 34, whereby then the intake valves according to the contour of the second cam 32 are actuated. All first and second Rocker arms 31, 33 for the intake valves of a row of cylinders are mounted on a common axis 35, the contains a channel 36 through which a pressure medium is supplied can be that the coupling pin 34 against the Force a spring 37 in the clutch position.

Wie aus Fig. 2 ersichtlich ist, erstrecken sich die Einlaßsammelkanäle 5 nach außen und oben zur Oberseite 37 des Zylinderkopfes. Jedem Einlaß-Sammelkanal 5 ist ein Einspritzventil 38 zugeordnet, das in Richtung auf die drei Einlaßventile 7 bzw. 7' spritzt. Auf die Oberseite 37 des Zylinderkopfes 3 ist eine Zylinderkopfhaube 39 aufgesetzt. Die Einlaß-Sammelkanäle 5 setzen sich in Kanälen 40 in der Zylinderkopfhaube 39 fort, die mit einem nicht gezeigten Ansaugverteiler in Verbindung stehen. As can be seen from Fig. 2, the inlet manifolds extend 5 outwards and upwards to the top 37 of the Cylinder head. Each inlet manifold 5 is an injection valve 38 assigned that towards the three Inlet valves 7 and 7 'injected. On the top 37 of the A cylinder head cover 39 is placed on the cylinder head 3. The inlet manifolds 5 sit in channels 40 in the Cylinder head cover 39 continues with a not shown Intake manifold are connected.

Die Kettenräder 20 und 22, 22' haben gleichen Durchmesser. Dieser Durchmesser kann kleiner sein als der Durchmesser des Auslaßnockenwellen-Antriebsrades 16. Dadurch kann die Baubreite des Zylinderkopfes 3 im Bereich des Nockenwellenantriebs, die maßgeblich von dem Durchmesser der Zahnräder 22, 22' bestimmt ist, relativ klein gehalten werden.The sprockets 20 and 22, 22 'have the same diameter. This diameter can be smaller than the diameter of the exhaust camshaft drive wheel 16. This can Overall width of the cylinder head 3 in the area of the camshaft drive, which depend largely on the diameter of the gears 22, 22 'is determined to be kept relatively small.

Claims (5)

  1. Multi cylinder internal combustion engine whose cylinders (1 and 2) are arranged in two rows, the cylinders (1) of one row being staggered with respect to the cylinders (2) of the other row and the longitudinal centre axes of the cylinders (1) of the one row forming an angle with respect to the longitudinal centre axes of the cylinders (2) of the other row
    having a cylinder head (3) which has for each cylinder at least one inlet valve (7, 7') and at least one exhaust valve (11, 11') which are actuated by cam shafts (12, 13, 14) driven by the crank shaft, the exhaust valves (11, 11') of all the cylinders (1, 2) being arranged in two exhaust valve rows (A, B) extending in the longitudinal direction of the engine, characterised by the following features:
    (a) the exhaust valve rows (A, B) are disposed on both sides of and near the plane of symmetry (S) that extends between the cylinder rows, whereas the inlet valves (7, 7') are arranged towards the outside,
    (b) a common exhaust camshaft (14) disposed in the plane of symmetry (S) is provided for the two exhaust valve rows (A, B), and for the inlet valves (7, 7') of each cylinder row there is provided a separate outwardly disposed inlet camshaft (15, 15'),
    (c) the exhaust ducts (8, 8') of the cylinders (1, 2) of each cylinder row extend from the combustion chamber side of the respective exhaust apertures (10, 10') over the respective neighbouring cylinder row (1, 2) towards the respective cylinder head side.
  2. Multi cylinder internal combustion engine according to claim 1, characterised in that with two exhaust valves (11, 11') per cylinder, the two exhaust ducts (8, 8') are in each case combined into a collective exhaust duct (9, 9').
  3. Multi cylinder internal combustion engine according to claim 1 or 2, characterised in that only the exhaust cam shaft (14) is directly driven from the crank shaft and that a regulating device (17) is provided on the exhaust cam shaft for varying the angular setting of the inlet camshafts (15, 15') relatively to the crank shaft and has a driver means (18) connected rotationally fast with the exhaust cam shaft (14) and a driven means (19) rotatable with respect to the driver means (18) and in connection with both inlet camshafts (15, 15') by way of a traction drive (20, 21, 22, 22').
  4. Multi cylinder internal combustion engine according to claim 3, characterised in that the traction drive is a chain drive and that the driven means (19) of the regulating device and the inlet camshaft (15, 15') have chain wheels (20, 22, 22') of the same diameter which is smaller than the diameter of the drive wheel (16) that is connected to the exhaust cam shaft (14) and is in driving communication with the crank shaft.
  5. Multi cylinder internal combustion engine according to claim 3 or 4, characterised in that the driver means (18) of the regulating device (17) carries the drive wheel (16) of the exhaust cam shaft (14).
EP95903790A 1993-12-24 1994-12-02 Multi-cylinder internal-combustion engine Expired - Lifetime EP0736133B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4344501 1993-12-24
DE4344501A DE4344501A1 (en) 1993-12-24 1993-12-24 Multi-cylinder internal combustion engine
PCT/EP1994/004013 WO1995018290A1 (en) 1993-12-24 1994-12-02 Multi-cylinder internal-combustion engine

Publications (2)

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EP0736133A1 EP0736133A1 (en) 1996-10-09
EP0736133B1 true EP0736133B1 (en) 1998-06-17

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EP95903790A Expired - Lifetime EP0736133B1 (en) 1993-12-24 1994-12-02 Multi-cylinder internal-combustion engine

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US (1) US5622143A (en)
EP (1) EP0736133B1 (en)
JP (1) JPH09502782A (en)
DE (2) DE4344501A1 (en)
WO (1) WO1995018290A1 (en)

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US5806499A (en) * 1997-03-18 1998-09-15 Cummins Engine Company, Inc. Dedicated overhead cam shaft for unit injector
GB2330893A (en) * 1997-11-03 1999-05-05 Mechadyne Int Plc Phase change mechanism
US6016775A (en) * 1998-09-14 2000-01-25 Detroit Diesel Corporation Two-cylinder head and narrow vee-type internal combustion engine including same
US6250263B1 (en) 1999-04-28 2001-06-26 Mark Sisco Dual piston cylinder configuration for internal combustion engine
EP1611330A4 (en) * 2003-01-22 2010-06-16 Abraham E Karem Fail-operational internal combustion engine
WO2004106761A2 (en) * 2003-05-28 2004-12-09 The Boeing Company Torque dividing gear drive system and method of driving an output gear
JP6637357B2 (en) * 2016-03-28 2020-01-29 本田技研工業株式会社 Power unit
DE102016117253B4 (en) 2016-09-14 2018-04-19 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Camshaft arrangement for internal combustion engines with VR cylinder arrangement

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IT1093715B (en) * 1978-03-24 1985-07-26 Alfa Romeo Spa TIMING VARIATOR OF THE DISTRIBUTION FOR INTERNAL COMBUSTION ALTERNATIVE ENGINE
JPS61275506A (en) * 1985-05-29 1986-12-05 Mazda Motor Corp Engine cam shaft driving device
JPH0672549B2 (en) * 1986-04-18 1994-09-14 マツダ株式会社 V-6 engine
DE3831333A1 (en) * 1988-09-15 1990-03-29 Audi Ag Multicylinder internal combustion engine
JP2690968B2 (en) * 1988-09-30 1997-12-17 ヤマハ発動機株式会社 V-type engine cooling system
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DE4002080A1 (en) * 1990-01-25 1991-08-01 Opel Adam Ag INTERNAL COMBUSTION ENGINE
DE4042415A1 (en) * 1990-09-28 1992-11-19 Daimler Benz Ag IC engine with cylinder banks in V-formation - has two-part intake conduit, located above exhaust collection pipes, both within V-space
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US5533586A (en) * 1994-02-01 1996-07-09 Arctco, Inc. Adjustable suspension system

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DE59406296D1 (en) 1998-07-23
DE4344501A1 (en) 1995-06-29
US5622143A (en) 1997-04-22
JPH09502782A (en) 1997-03-18
WO1995018290A1 (en) 1995-07-06
EP0736133A1 (en) 1996-10-09

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