EP0895563B1 - Reciprocating internal combustion engine - Google Patents

Reciprocating internal combustion engine Download PDF

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Publication number
EP0895563B1
EP0895563B1 EP97914224A EP97914224A EP0895563B1 EP 0895563 B1 EP0895563 B1 EP 0895563B1 EP 97914224 A EP97914224 A EP 97914224A EP 97914224 A EP97914224 A EP 97914224A EP 0895563 B1 EP0895563 B1 EP 0895563B1
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EP
European Patent Office
Prior art keywords
row
cylinders
rows
internal combustion
combustion engine
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP97914224A
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German (de)
French (fr)
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EP0895563A1 (en
Inventor
Hermann Deutsch
Frank Metzner
Frank Meyer-Hessing
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Volkswagen AG
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Volkswagen AG
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    • 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
    • F02B75/224—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders in fan arrangement
    • 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
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/1812—Number of cylinders three
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/1832—Number of cylinders eight
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/184—Number of cylinders ten
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/1848—Number of cylinders twelve

Definitions

  • the invention relates to a reciprocating internal combustion engine with several, along two at an angle to each other rows of cylinders according to the preamble of Claim 1.
  • a generic internal combustion engine is known from DE-Z MTZ Motortechnische Zeitschrift 52, 1991, No. 3, pages 100 ff.
  • the VR engine described there and produced by the applicant in large series has cylinders combined in two rows, these two rows being at a comparatively narrow fork angle to one another.
  • this cylinder arrangement offers the advantage that only a single cylinder crankcase with all the cylinders combined therein in one block and only one cylinder head common to all cylinders is required. Due to the offset of the two rows of cylinders in the longitudinal direction to each other, the overall length of such a VR engine with z. B.
  • a 16-cylinder engine with an H-shaped cylinder arrangement has become known from the DE book Air-Cooled Vehicle Engines, Mackerle, Jehlicka, Moebus, Franksche Verlagbuch Kunststoff Stuttgart, page 509.
  • a compact arrangement is achieved here by stacking two 8-cylinder boxer engines. These each work on their own crankshaft, which, coupled together, operate a single-shaft output.
  • the two opposite, 4-cylinder rows have no longitudinal offset to each other, since the two connecting rods of opposing cylinders work on a common crank pin of the crankshaft by using a connecting rod.
  • pages 515 ff is another compact arrangement in an X shape known.
  • two are mirror images of each other Rows of cylinders arranged in a V-shape to each other, all of which are not restricted
  • the crank mechanism works with a common crankshaft, i.e. all cylinder longitudinal axes intersect the crankshaft's central longitudinal axis.
  • the crankshaft only points four offsets since there is a main connecting rod with three secondary connecting rods on each of these crank pins works, i.e. the four rows of cylinders have no longitudinal offset to each other on.
  • the invention has for its object a generic reciprocating internal combustion engine with several, at an angle to each other and a longitudinal offset to each other having cylinders in such a way that under stress a construction space as small as possible, a compact arrangement of a comparatively large one Number of cylinders is made possible.
  • the aim is to ensure a fresh air supply or the discharge of the exhaust gases, as well as a perfect drive of the gas exchange Gas exchange valves can be guaranteed.
  • the invention solves this problem in a generic internal combustion engine by an arrangement of two further, also V-shaped rows of cylinders, one of these rows of cylinders being arranged in the V-space between the first and second rows and the further, fourth row outside this V-space lies, whereby the cylinders of all rows work on a common crankshaft.
  • the even number of rows of cylinders also ensures a symmetrical arrangement of lines for the air supply and for exhaust gases.
  • this provides the basis for a modular construction of a series of internal combustion engines of the same type with different numbers of cylinders while maintaining the fundamentally compact arrangement and while maintaining existing lines. Both even and odd number of cylinders can be used in each row.
  • An advantageous embodiment is to achieve a comparatively simple structure provided that the additional, third and fourth rows are longitudinally offset from one another and to the first two rows of cylinders.
  • uniform connecting rods can be used.
  • the between the first and second row of cylinders and the fork angles formed between the third and fourth row of cylinders are identical in size and that is the V-spaces formed by this fork angle by a certain cylinder angle are arranged rotated to each other.
  • This cylinder angle is chosen so that the first and third or second and fourth rows mirror-symmetrical with respect to the other two rows to one Crankshaft receiving center plane of the internal combustion engine. Under the assumption a perpendicular center plane thus results on both sides of this plane each cylinder rows arranged in a V-shape, the cylinder angle within this V-shaped rows is chosen to be comparatively small.
  • crank mechanism of this internal combustion engine is limited, that is Cylinder axes of the two rows on one side of the median plane intersect vertical arrangement of the median plane below this and on the opposite Page. This further shortens the internal combustion engine by pushing one into the other of the cylinders assigned to the two rows.
  • each crank has two connecting rods offset from one another.
  • the connecting rods of two work around the fork angle offset cylinders of the first and third or second and fourth rows.
  • the cylinder rows each have three cylinders and the other two each have two cylinders.
  • the rows with the larger number of cylinders are preferably offset from one another by the fork angle.
  • control drive of the Internal combustion engine can have the two combined rows of cylinders on each side the central plane can be made identical overall, which creates further advantageous effects in terms of component expense, assembly, etc. can be achieved.
  • a reciprocating piston internal combustion engine hereinafter referred to only as an internal combustion engine, has a total of four rows R1, R2, R3, R4 of cylinders, two of these rows R1, R3 and R2, R 4 being arranged on one of the two sides S1, S2 of a central plane ME are, which receives a crankshaft axis 1.
  • the row R1 assigned to the side S1 and the row R2 assigned to the side S2 are V-shaped to one another at a fork angle ⁇ 1 and thus define a first V-space V1 between them.
  • the two further cylinder rows R3 and R4 are assigned to the sides S1 and S2 and are at a fork angle ⁇ 2, defining another V-space V2, to one another.
  • the third row R3 is in the first V-space V1, while the fourth row R4 is arranged outside of this space V1.
  • the rows R1 and R3 lying on the side S1 are combined to form a group G1, cylinder axes ZR1 of the first row and cylinder axes ZR3 of the third row again being at a V-shaped cylinder angle ⁇ G1 to one another.
  • the size of the fork angles ⁇ 1 and ⁇ 2 is chosen to be identical, as is the size of the cylinder angles ⁇ G1 and ⁇ G2, the entire arrangement with respect to the central plane ME being such that the groups G1 and G2 are each symmetrical to this central plane ME and thereby the rows R1, R3 and R2, R4 of these groups G1 and G2 are each arranged mirror-symmetrically to this plane ME.
  • cylinder axes ZR1 and ZR3 have respectively ZR2 and ZR4 are identical to each other along the crankshaft axis 1 Row offset 2 on.
  • the two groups G1 and G2 in turn have a group offset 3 along this crankshaft axis 1.
  • the cylinder axes ZR1 to ZR4 thus each lie in one of four sectional planes SE1 to SE4 formed perpendicular to the central plane ME.
  • the cylinders Z1 and Z3 are assigned to the first row R1, the cylinders Z2 and Z4 to the third row R3, the cylinders Z5 and Z7 to the second row R2 and the cylinders Z6 and Z8 to the fourth row R4.
  • a crankshaft 4 of the internal combustion engine has a total of four crankings 5, 6, 7, 8 and is supported in a total of five main bearings 9 of a crankcase 10.
  • two cylinders each work on one of the cranks by means of the connecting rods 11 assigned to them, the two conrod bearings 12, 13 of a crank having an offset by a difference angle ⁇ winkel.
  • the cylinders which are staggered relative to each other by the group offset 3 and are assigned to one of the V-spaces V1 or V2, work on one of the offsets.
  • the connecting rods 11 of the cylinders Z1 and Z5 lying in the sectional planes SE1 and SE2 are spaced apart from one another by the offset 3 in the crank 5. Between the connecting rods 11 of cylinders Z5 and Z6 lying in the sectional plane SE2 and SE4 there is the row offset 2, usually referred to as the cylinder spacing.
  • the crank mechanism of the internal combustion engine is designed to be limited, that is to say the cylinder axes ZR1, ZR3 or ZR2, ZR4, which are at an angle to one another by the cylinder angle ⁇ G1 or ⁇ G2, do not intersect with the crankshaft axis 1 Intersection SP1 of the first group G1 on the side S2 on the side of the transverse plane QE facing away from the rows R1 and R3.
  • another intersection point SP2 of the second group G2 lies in mirror image with respect to the center plane ME. Because of the cranking of the crank mechanism, the maximum extension positions of the connecting rods 11 at top and bottom dead center OT and UT do not coincide with the respective cylinder axis ZR.
  • crank angle ⁇ occurring during the rotation of the crankshaft 4 is counted by the crankshaft axis 1, based on an unrestricted crank drive from a parallel 13 to the cylinder axis ZR, then TDC and TDC are achieved with a crank angle offset of ⁇ *. Due to the position of the intersection points SP1 and SP2 with respect to the transverse plane QE on the side facing away from the groups G1 and G2, a positive or negative setpoint is set, so that the bottom dead center UT and the top dead center OT after more or less than 180 ° crank angle ⁇ follows.
  • the selected setting enables the space to be moved closer together Cylinders within groups G1 and G2, so that the respective cylinders of these groups G1 and G2 are cast together in a common cylinder block 15 and 16, respectively can. These are common to one of the two rows of cylinders in a group Cylinder head 17 or 18 covered.
  • the interaction of the previously explained 8-cylinder arrangement is briefly based on one Numerical example explained.
  • the fork angles ⁇ 1 and ⁇ 2 are 72 °, the cylinder angles ⁇ G1 and ⁇ G2 each 15 °. Due to the symmetrical arrangement to the central plane ME the cylinder angles ⁇ G1 and ⁇ G2 also arise with respect to the bisector 19 the fork angle ⁇ 1 or ⁇ 2. Because of the four offsets 5 to lying on two levels 8 there is an ignition sequence between the individual cylinders at a crank angle of 90 ° ⁇ a. With a selected firing order in the order Z1-Z5-Z4-Z8-Z6-Z3-Z7-Z2, 2 in the crank star 20 according to FIG.
  • the offset within the individual Cranks 5 to 8 are dispensed with.
  • the rows R3 and R4 are three each Cylinder assigned, while the rows R1 and R2 each carry two cylinders. While here the previously described mirror-image arrangement of the angular positions mentioned the middle plane ME is preserved, the arrangement of the rows is not a mirror image, because on the three-cylinder row R3 lying on the side S1 initially has one on the side S2 two-cylinder row R2 follows.
  • a flywheel 25 is assigned to the crankshaft 4 on the output side. Adjacent to this is a chain drive for driving camshafts 27 and 28 of group G1 and camshafts 29 and 30 of group G2 arranged. These operate via cams 31 and 32 as Lift valves designed intake valves 33 and exhaust valves 34 with the interposition of Roller rocker arms 35, four lift valves being assigned to each cylinder Z1 to Z8.
  • An air intake system for ventilating the combustion chambers 40 of the internal combustion engine is essentially symmetrical to the central plane ME and is provided with collecting volumes 37 and 38 formed above the groups G1 and G2. Combustion air is fed via suction pipes 41 from the above-mentioned collecting volumes 37, 38 to inlet channels 41, all inlet channels 41 of a group G1 or G2 each opening into a flange 42 which is formed on the row R3 or R2 facing the central plane ME. All outlet channels 43 of the respective group G1 or G2 are led to flanges 44 of the rows R1 and R4, which are external to the central plane ME.
  • the cylinder blocks 15 and 16 are in one piece and of the same material as the crankcase 10 formed, the outer walls 45 in the region of the crankshaft axis 1 are drawn across the transverse plane QE.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

Die Erfindung betrifft eine Hubkolben-Brennkraftmaschine mit mehreren, entlang zweier unter einem Winkel zueinanderstehender Reihen von Zylindern gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a reciprocating internal combustion engine with several, along two at an angle to each other rows of cylinders according to the preamble of Claim 1.

Eine gattungsgemäße Brennkraftmaschine ist aus DE-Z MTZ Motortechnische Zeitschrift 52, 1991, Nr. 3, Seiten 100 ff bekannt. Der dort beschriebene und von der Anmelderin in Großserie produzierte, sogenannte VR-Motor weist in zwei Reihen zusammengefaßte Zylinder auf, wobei diese beiden Reihen unter einem vergleichsweise engen Gabelwinkel zueinander stehen. Gegenüber bekannten, V-förmigen Brennkraftmaschinen mit vergleichsweise großem Gabelwinkel bietet diese Zylinderanordnung den Vorteil, daß lediglich ein einziges Zylinderkurbelgehäuse mit allen darin in einem Block vereinigten Zylindern sowie lediglich ein allen Zylindern gemeinsamer Zylinderkopf benötigt wird. Durch den Versatz der beiden Zylinderreihen in Längsrichtung zueinander liegt die Baulänge eines solchen VR-Motors mit z. B. 6 Zylindern nur unwesentlich über der eines konventionellen 4-zylindrigen Reihenmotors, wobei jedoch gegenüber 6-zylindrigen, klassischen V-Brennkraftmaschinen eine erheblich geringere Baubreite beansprucht wird.
Die Zylinderbänke dieses Motors weisen einen Gabelwinkel von 15° zueinander auf und die jeweils drei Zylinderachsen einer Zylinderreihe liegen in einer gemeinsamen Ebene, welche sich in einem Abstand von 12,5 mm unterhalb der Kurbelwelle schneiden. Dieser geschränkte Kurbeltrieb führt zu einer weiteren Verkürzung des Motors.
Bezüglich der Geometrie des Kurbeltriebes und der verwendeten Kurbelwellenkröpfungslagen sowie der Zündfolgen sei auf die DE-Z MTZ, Motortechnische Zeitschrift 51, 1990, Nr. 10 verwiesen, welche sich detailliert mit diesem VR-Motorkonzept auseinandersetzt und dabei auch Vorschläge bezüglich der Verwendung von einer, zwei oder drei Nockenwellen im gemeinsamen Zylinderkopf zur Betätigung von jeweils zwei oder vier Ventilen je Brennraum unterbreitet. A generic internal combustion engine is known from DE-Z MTZ Motortechnische Zeitschrift 52, 1991, No. 3, pages 100 ff. The VR engine described there and produced by the applicant in large series has cylinders combined in two rows, these two rows being at a comparatively narrow fork angle to one another. Compared to known, V-shaped internal combustion engines with a comparatively large fork angle, this cylinder arrangement offers the advantage that only a single cylinder crankcase with all the cylinders combined therein in one block and only one cylinder head common to all cylinders is required. Due to the offset of the two rows of cylinders in the longitudinal direction to each other, the overall length of such a VR engine with z. B. 6 cylinders only slightly above that of a conventional 4-cylinder in-line engine, however, compared to 6-cylinder, classic V-internal combustion engines, a considerably smaller width is required.
The cylinder banks of this engine have a fork angle of 15 ° to each other and the three cylinder axes of each row of cylinders lie in a common plane, which intersect at a distance of 12.5 mm below the crankshaft. This limited crank drive leads to a further shortening of the engine.
With regard to the geometry of the crank mechanism and the crankshaft crank positions used and the firing sequences, reference is made to DE-Z MTZ, Motortechnische Zeitschrift 51, 1990, No. 10, which deals in detail with this VR engine concept and also suggests the use of a submitted two or three camshafts in the common cylinder head for actuating two or four valves per combustion chamber.

Zur Erzielung einer möglichst kompakten Zylinderanordnung hat es neben dem bereits zitierten VR-Konzept bereits weitere Lösungsansätze gegeben.
So ist aus dem DE-Buch Luftgekühlte Fahrzeugmotoren, Mackerle, Jehlicka, Moebus, Franksche Verlagsbuchhandlung Stuttgart, Seite 509, ein 16-zylindriger Motor mit H-förmiger Zylinderanordnung bekannt geworden. Eine kompakte Anordnung wird hier durch das Übereinanderanordnen von zwei 8-zylindr- igen Boxerbrennkraftmaschinen erzielt. Diese arbeiten jeweils auf eine eigene Kurbelwelle, welche aneinander gekoppelt einen einwelligen Abtrieb bedienen. Die beiden sich jeweils gegenüberliegenden, 4-zylindrigen Reihen weisen keinen Längsversatz zueinander auf, da die beiden Pleuel von sich gegenüberliegenden Zylindern durch die Verwendung eines Gabelpleuels auf einen gemeinsamen Hubzapfen der Kurbelwelle arbeiten.In addition to the VR concept already cited, there have already been other possible solutions for achieving the most compact possible cylinder arrangement.
A 16-cylinder engine with an H-shaped cylinder arrangement has become known from the DE book Air-Cooled Vehicle Engines, Mackerle, Jehlicka, Moebus, Franksche Verlagbuchhandlung Stuttgart, page 509. A compact arrangement is achieved here by stacking two 8-cylinder boxer engines. These each work on their own crankshaft, which, coupled together, operate a single-shaft output. The two opposite, 4-cylinder rows have no longitudinal offset to each other, since the two connecting rods of opposing cylinders work on a common crank pin of the crankshaft by using a connecting rod.

Aus der gleichen Quelle, Seiten 515 ff ist eine weitere, kompakte Anordnung in X-Form bekannt. Bezüglich einer vertikalen Ebene sind spiegelbildlich zueinander jeweils zwei Reihen von Zylindern V-förmig zueinander angeordnet, welche alle auf einen nicht geschränkten Kurbeltrieb mit einer gemeinsamen Kurbelwelle arbeiten, das heißt alle Zylinderlängsachsen schneiden die Kurbelwellenmittellängsachse. Die Kurbelwelle weist lediglich vier Kröpfungen auf, da auf jeden dieser Hubzapfen ein Hauptpleuel mit drei Nebenpleuel arbeitet, das heißt die insgesamt vier Zylinderreihen weisen keinen Längsversatz zueinander auf.From the same source, pages 515 ff is another compact arrangement in an X shape known. With respect to a vertical plane, two are mirror images of each other Rows of cylinders arranged in a V-shape to each other, all of which are not restricted The crank mechanism works with a common crankshaft, i.e. all cylinder longitudinal axes intersect the crankshaft's central longitudinal axis. The crankshaft only points four offsets since there is a main connecting rod with three secondary connecting rods on each of these crank pins works, i.e. the four rows of cylinders have no longitudinal offset to each other on.

Eine weitere kompakte Anordnung von mehreren Zylindern einer Brennkraftmaschine in W-Form ist aus der DE-Z sportauto, März 1988, Nr. 3, Seiten 90 ff bekannt. Diese vergleichsweise breit, jedoch kurzbauende Zylinderanordnung weist drei 4-zylindrige Reihen auf, von denen eine mittige in einer vertikalen Ebene liegt, während die anderen beiden V-förmig, mit der ersten Reihe als Winkelhalbierender, angeordnet sind. Die drei Reihen weisen zueinander einen Längsversatz auf, da jeweils drei Zylinder mit ihren Pleueln nebeneinanderliegend auf einen gemeinsamen Hubzapfen der Kurbelwelle arbeiten.
Problematisch bei einer solchen Anordnung ist die gleichmäßige Versorgung der den Zylindern zugeordneten Brennräume mit Frischgemisch sowie die Abfuhr der Verbrennungsgase, da sich in dem V-Raum auf einer Seite der horizontalen Ebene nur Einlaßkanäle für zwei Zylinderreihen befinden, während auf der anderen Seite in diesem V-Raum die einer der Zylinderreihen zugeordneten Einlaßkanäle und die Auslaßkanäle der anderen Zylinderreihe angeordnet werden müssen.Another compact arrangement of several cylinders of an internal combustion engine in a W shape is known from DE-Z sports car, March 1988, No. 3, pages 90 ff. This comparatively wide, but short cylinder arrangement has three 4-cylinder rows, one of which lies in the middle in a vertical plane, while the other two are arranged in a V-shape, with the first row as an angle bisector. The three rows have a longitudinal offset from each other, since three cylinders with their connecting rods work side by side on a common crank pin of the crankshaft.
The problem with such an arrangement is the uniform supply of the combustion chambers assigned to the cylinders with fresh mixture and the removal of the combustion gases, since there are only inlet ducts for two rows of cylinders in the V-space on one side of the horizontal plane, while on the other side in this V -Space the intake ports assigned to one of the rows of cylinders and the exhaust ports of the other row of cylinders must be arranged.

Letztendlich ist es aus der DE-Z MTZ Motortechnische Zeitschrift 1940, Heft 2, Seiten 52 und 53 bekannt, zwei V-förmige Brennkraftmaschinen zu einem Doppel-V-Motor derart zusammenzufassen, daß die Winkelhalbierenden der jeweils unter einem Zylinderwinkel von 60° stehenden V-Reihen einen Winkel von 90° zueinander bilden. Die jeweils beiden Reihen eines V-Raumes arbeiten dabei auf eine eigene Kurbelwelle.Ultimately, it is from DE-Z MTZ Motortechnische Zeitschrift 1940, Issue 2, pages 52 and 53 known two V-shaped internal combustion engines to a double V engine such summarize that the bisector of each at a cylinder angle of 60 ° standing V rows form an angle of 90 ° to each other. The two rows of a V-space work on their own crankshaft.

Der Erfindung liegt die Aufgabe zugrunde, eine gattungsgemäße Hubkolben-Brennkraftmaschine mit mehreren, unter einem Winkel zueinander stehenden und einen Längsversatz zueinander aufweisenden Zylindern derart weiterzubilden, daß unter Beanspruchung eines möglichst geringen Bauraumes eine kompakte Anordnung einer vergleichsweise großen Zylinderanzahl ermöglicht wird. Zugleich soll hierbei eine einwandfreie Zufuhr von Frischluft bzw. das Ableiten der Abgase, sowie ein einwandfreier Antrieb der den Gaswechsel bereitstellenden Gaswechselventile gewährleistet sein.The invention has for its object a generic reciprocating internal combustion engine with several, at an angle to each other and a longitudinal offset to each other having cylinders in such a way that under stress a construction space as small as possible, a compact arrangement of a comparatively large one Number of cylinders is made possible. At the same time, the aim is to ensure a fresh air supply or the discharge of the exhaust gases, as well as a perfect drive of the gas exchange Gas exchange valves can be guaranteed.

Die Lösung dieser Aufgabe gelenkt mit den Merkmalen des Patentanspruches 1.
Vorteilhafte Ausgestaltungen der Erfindung sind in den abhängigen Ansprüchen angegeben.The solution to this problem is directed with the features of claim 1.
Advantageous embodiments of the invention are specified in the dependent claims.

Die Erfindung löst die gestellte Aufgabe bei einer gattungsgemäßen Brennkraftmaschine durch eine Anordnung von zwei weiteren, ebenfalls V-förmig zueinanderstehenden Reihen von Zylindern, wobei eine dieser Zylinderreihen in dem V-Raum zwischen der ersten und zweiten Reihe angeordnet ist und die weitere, vierte Reihe außerhalb dieses V-Raumes liegt, wobei die Zylinder aller Reihen auf eine gemeinsame Kurbelwelle arbeiten. Bei geeigneter Wahl der zwischen den einzelnen Reihen liegenden Winkel ist es hierdurch möglich, eine kompakte Anordnung der Zylinder zu erzielen, wodurch insbesondere die Baulänge in Richtung der Kurbelwellenachse kurz gehalten werden kann. Durch die gradzahlige Anzahl der Reihen von Zylindern ist ebenfalls eine symmetrische Anordnung von Leitungen für die Luftzufuhr sowie für Abgase gewährleistet.
Weiterhin ist hiermit die Grundlage für einen baukastenartigen Aufbau einer Reihe von gleichartigen Brennkraftmaschinen mit unterschiedlicher Zylinderanzahl unter Wahrung der grundsätzlich kompakten Anordnung und unter Beibehaltung von vorhandenen Leitungen gegeben. Hierbei können sowohl gradzahlige wie auch ungradzahlige Zylinderanzahlen in jeder Reihe zur Anwendung kommen.The invention solves this problem in a generic internal combustion engine by an arrangement of two further, also V-shaped rows of cylinders, one of these rows of cylinders being arranged in the V-space between the first and second rows and the further, fourth row outside this V-space lies, whereby the cylinders of all rows work on a common crankshaft. With a suitable choice of the angles lying between the individual rows, it is thereby possible to achieve a compact arrangement of the cylinders, as a result of which in particular the overall length in the direction of the crankshaft axis can be kept short. The even number of rows of cylinders also ensures a symmetrical arrangement of lines for the air supply and for exhaust gases.
Furthermore, this provides the basis for a modular construction of a series of internal combustion engines of the same type with different numbers of cylinders while maintaining the fundamentally compact arrangement and while maintaining existing lines. Both even and odd number of cylinders can be used in each row.

In vorteilhafter Ausgestaltung ist zur Erzielung eines vergleichsweise einfachen Aufbaus vorgesehen, daß die zusätzlichen, dritten und vierten Reihen einen Längsversatz zueinander und zu den beiden ersten Reihen von Zylindern aufweisen. Somit können unter Vermeidung von vergleichsweise kompliziert und teuer zu fertigenden Gabelpleueln für alle Zylinder einheitliche Pleuel verwendet werden. An advantageous embodiment is to achieve a comparatively simple structure provided that the additional, third and fourth rows are longitudinally offset from one another and to the first two rows of cylinders. Thus, while avoiding of comparatively complicated and expensive fork connecting rods for all cylinders uniform connecting rods can be used.

Bevorzugt ist vorgesehen, daß der zwischen der ersten und zweiten Zylinderreihe und der zwischen der dritten und vierten Zylinderreihe gebildete Gabelwinkel jeweils identisch groß ist und das die durch diesen Gabelwinkel gebildeten V-Räume um einen bestimmten Zylinderwinkel zueinander verdreht angeordnet sind. Dieser Zylinderwinkel ist dabei so gewählt, daß die unter diesem Winkel zueinanderstehenden ersten und dritten bzw. zweiten und vierten Reihen spiegelsymmetrisch bezüglich der jeweils anderen beiden Reihen zu einer die Kurbelwelle aufnehmenden Mittelebene der Brennkraftmaschine liegen. Unter der Annahme einer senkrecht verlaufenden Mittelebene ergeben sich somit zu beiden Seiten dieser Ebene jeweils V-förmig zueinander angeordnete Zylinderreihen, wobei der Zylinderwinkel innerhalb dieser V-förmigen Reihen vergleichsweise klein gewählt wird.It is preferably provided that the between the first and second row of cylinders and the fork angles formed between the third and fourth row of cylinders are identical in size and that is the V-spaces formed by this fork angle by a certain cylinder angle are arranged rotated to each other. This cylinder angle is chosen so that the first and third or second and fourth rows mirror-symmetrical with respect to the other two rows to one Crankshaft receiving center plane of the internal combustion engine. Under the assumption a perpendicular center plane thus results on both sides of this plane each cylinder rows arranged in a V-shape, the cylinder angle within this V-shaped rows is chosen to be comparatively small.

In weiterer bevorzugter Ausgestaltung der Erfindung ist gemäß Anspruch 4 vorgesehen, daß der Kurbeltrieb dieser Brennkraftmaschine geschränkt ausgeführt ist, das heißt die Zylinderachsen der beiden Reihen auf einer Seite der Mittelebene schneiden sich bei lotrechter Anordnung der Mittelebene unterhalb dieser und auf der gegenüberliegenden Seite. Hierdurch ist eine weitere Verkürzung der Brennkraftmaschine durch Ineinanderschieben der den jeweils zwei Reihen zugeordneten Zylindern möglich.In a further preferred embodiment of the invention it is provided according to claim 4 that the crank mechanism of this internal combustion engine is limited, that is Cylinder axes of the two rows on one side of the median plane intersect vertical arrangement of the median plane below this and on the opposite Page. This further shortens the internal combustion engine by pushing one into the other of the cylinders assigned to the two rows.

Zur Erzielung von gleichmäßigen Zündabständen auch bei unterschiedlicher Zylinderanzahl kann bei z. B. jeweils zwei Zylindern pro Zylinderreihe, also insgesamt 8 Zylindern, ein sich aus dem Bild der Kurbelwelle ergebender Kurbelstern mit 4 Kröpfungen vorgesehen sein, wobei jede Kröpfung zwei zueinander versetzte Lager für Pleuel aufweist. Auf diese gemeinsame, versetzte Kröpfung arbeiten jeweils die Pleuel von zwei um den Gabelwinkel zueinander versetzter Zylinder der ersten und dritten bzw. zweiten und vierten Reihe.To achieve even firing intervals even with different numbers of cylinders can at z. B. two cylinders per cylinder row, that is a total of 8 cylinders, one from the picture of the crankshaft resulting crank star with 4 crankings, each crank has two connecting rods offset from one another. To this Common, offset cranking, the connecting rods of two work around the fork angle offset cylinders of the first and third or second and fourth rows.

Alternativ kann beispielsweise zur Erzielung einer insgesamt 10-zylindrigen Brennkraftmaschine vorgesehen sein, daß zwei der Zylinderreihen jeweils drei Zylinder und die beiden weiteren jeweils zwei Zylinder aufweisen.
Bevorzugt ist dabei zur Verwendung möglichst gleicher Teile und zur Erzielung einer symmetrischen Anordnung vorgesehen, die Reihen mit der größeren Anzahl von Zylindern um den Gabelwinkel zueinander versetzt anzuordnen.Alternatively, for example, to achieve an overall 10-cylinder internal combustion engine, it can be provided that two of the cylinder rows each have three cylinders and the other two each have two cylinders.
In order to use the same parts as possible and to achieve a symmetrical arrangement, the rows with the larger number of cylinders are preferably offset from one another by the fork angle.

In weiterer, vorteilhafter Ausgestaltung kann vorgesehen sein, daß die zu beiden Seiten der Mittelebene liegenden und um den Zylinderwinkel zueinander versetzten Reihen jeweils zu einem zusammenhängenden Zylinderblock zusammengefaßt sind, welcher von einem diesen beiden Reihen gemeinsamen Zylinderkopf abgedeckt sein kann. In a further, advantageous embodiment, it can be provided that the Rows lying in the middle plane and offset by the cylinder angle to each other a coherent cylinder block are summarized, which of a these two rows common cylinder head can be covered.

Zur Erzielung einer bauraumoptimalen Anordnung beispielsweise des Steuertriebes der Brennkraftmaschine können die beiden zusammengefaßten Zylinderreihen zu jeder Seite der Mittelebene insgesamt identisch ausgebildet sein, wodurch weitere vorteilhafte Effekte hinsichtlich Bauteilaufwand, Montage etc. erzielbar sind.To achieve an arrangement that is optimal in terms of installation space, for example of the control drive of the Internal combustion engine can have the two combined rows of cylinders on each side the central plane can be made identical overall, which creates further advantageous effects in terms of component expense, assembly, etc. can be achieved.

Weitere Vorteile der Erfindung ergeben sich aus dem nachfolgend anhand einer Zeichnung näher erläuterten Ausführungsbeispiel.
Es zeigen:

  • Figur 1 eine schematische Draufsicht auf eine erfindungsgemäße Brennkraftmaschine,
  • Figur 2 eine schematische Seitenansicht zu Figur 1 des Kurbeltriebes und
  • Figur 3 einen Querschnitt durch eine Brennkraftmaschine.
    • Further advantages of the invention result from the exemplary embodiment explained in more detail below with reference to a drawing.
    Show it:
  • FIG. 1 shows a schematic top view of an internal combustion engine according to the invention,
  • Figure 2 is a schematic side view of Figure 1 of the crank mechanism and
  • Figure 3 shows a cross section through an internal combustion engine.

    • Eine im weiteren nur als Brennkraftmaschine bezeichnete Hubkolben-Brennkraflmaschine weist insgesamt vier Reihen R1, R2, R3, R4 von Zylindern auf, wobei jeweils zwei dieser Reihen R1, R3 und R2, R 4 auf einer der beiden Seiten S1, S2 einer Mittelebene ME angeordnet sind, welche eine Kurbelwellenachse 1 aufnimmt.
    Die der Seite S1 zugeordnete Reihe R1 und die der Seite S2 zugeordnete Reihe R2 stehen unter einem Gabelwinkel δ1 V-förmig zueinander und definieren zwischen sich somit einen ersten V-Raum V1.
    In analoger Weise sind die beiden weiteren Zylinderreihen R3 und R4 den Seiten S1 und S2 zugeordnet und stehen unter einem Gabelwinkel δ2, einen weiteren V-Raum V2 definierend, zueinander. Somit steht die dritte Reihe R3 in dem ersten V-Raum V1, während die vierte Reihe R4 außerhalb dieses Raumes V1 angeordnet ist.    A reciprocating piston internal combustion engine, hereinafter referred to only as an internal combustion engine, has a total of four rows R1, R2, R3, R4 of cylinders, two of these rows R1, R3 and R2, R 4 being arranged on one of the two sides S1, S2 of a central plane ME are, which receives a crankshaft axis 1.
    The row R1 assigned to the side S1 and the row R2 assigned to the side S2 are V-shaped to one another at a fork angle δ1 and thus define a first V-space V1 between them.
    In an analogous manner, the two further cylinder rows R3 and R4 are assigned to the sides S1 and S2 and are at a fork angle δ2, defining another V-space V2, to one another. Thus, the third row R3 is in the first V-space V1, while the fourth row R4 is arranged outside of this space V1.

    Die auf der Seite S1 liegenden Reihen R1 und R3 sind zu einer Gruppe G1 zusammengefaßt, wobei Zylinderachsen ZR1 der ersten Reihe und Zylinderachsen ZR3 der dritten Reihe wiederum unter einem V-förmigen Zylinderwinkel αG1 zueinander stehen.
    Die Größe der Gabelwinkel δ1 und δ2 ist dabei identisch gewählt ebenso wie die Größe der Zylinderwinkel αG1 und αG2, wobei die gesamte Anordnung bezüglich der Mittelebene ME so getroffen ist, daß die Gruppen G1 und G2 jeweils symmetrisch zu dieser Mittelebene ME liegen und dadurch die Reihen R1, R3 bzw. R2, R4 dieser Gruppen G1 bzw. G2 jeweils spiegelsymmetrisch zu dieser Ebene ME angeordnet sind.    The rows R1 and R3 lying on the side S1 are combined to form a group G1, cylinder axes ZR1 of the first row and cylinder axes ZR3 of the third row again being at a V-shaped cylinder angle αG1 to one another.
    The size of the fork angles δ1 and δ2 is chosen to be identical, as is the size of the cylinder angles αG1 and αG2, the entire arrangement with respect to the central plane ME being such that the groups G1 and G2 are each symmetrical to this central plane ME and thereby the rows R1, R3 and R2, R4 of these groups G1 and G2 are each arranged mirror-symmetrically to this plane ME.

    Innerhalb der Gruppen G1 und G2 weisen die Zylinderachsen ZR1 und ZR3 beziehungsweise ZR2 und ZR4 zueinander entlang der Kurbelwellenachse 1 einen identischen Reihenversatz 2 auf. Within groups G1 and G2, cylinder axes ZR1 and ZR3 have respectively ZR2 and ZR4 are identical to each other along the crankshaft axis 1 Row offset 2 on.

    Die beiden Gruppen G1 und G2 wiederum weisen entlang dieser Kurbelwellenachse 1 einen Gruppenversatz 3 auf.
    Die Zylinderachsen ZR1 bis ZR4 liegen somit jeweils in einer von vier senkrecht zur Mittelebene ME ausgebildeten Schnittebenen SE1 bis SE4.    The two groups G1 and G2 in turn have a group offset 3 along this crankshaft axis 1.
    The cylinder axes ZR1 to ZR4 thus each lie in one of four sectional planes SE1 to SE4 formed perpendicular to the central plane ME.

    Das Zusammenwirken der einzelnen Zylinder im Kurbeltrieb sei anhand einer 8-zylindrigen Ausführung der Brennkraftmaschine erläutert. Gemäß Figur 1 sind hierbei die Zylinder Z1 und Z3 der ersten Reihe R1, die Zylinder Z2 und Z4 der dritten Reihe R3, die Zylinder Z5 und Z7 der zweiten Reihe R2 und die Zylinder Z6 und Z8 der vierten Reihe R4 zugeordnet.
    Eine Kurbelwelle 4 der Brennkraftmaschine weist insgesamt vier Kröpfungen 5, 6, 7, 8 auf und ist in insgesamt fünf Hauptlagern 9 eines Kurbelgehäuses 10 abgestützt. Zur Erzielung einer gleichmäßigen und komfortablen Zündfolge arbeiten jeweils zwei Zylinder mittels der ihnen zugeordneten Pleuel 11 auf eine der Kröpfungen, wobei die beiden Pleuellager 12, 13 einer Kröpfung einen Versatz um einen Differenzwinkel Δϕ aufweisen.
    Die jeweils um den Gruppenversatz 3 zueinander gestaffelten und einem der V-Räume V1 bzw. V2 zugeordneten Zylinder arbeiten auf eine der Kröpfungen. Somit sind die Pleuel 11 der Zylinder Z1 und Z5 mit der Kröpfung 5, die Zylinder Z2 und Z6 mit der Kröpfung 6, die Zylinder Z3 und Z7 mit der Kröpfung 7 und die Zylinder Z4 und Z8 mit der Kröpfung 8 verbunden. Wie aus Figur 2, rechts ersichtlich, sind die in den Schnittebenen SE1 und SE2 liegenden Pleuel 11 der Zylinder Z1 und Z5 in der Kröpfung 5 um den Gruppenversatz 3 zueinander beabstandet. Zwischen den in der Schnittebene SE2 und SE4 liegenden Pleueln 11 von Zylinder Z5 und Z6 liegt der, üblicherweise als Zylinderabstand bezeichnete, Reihen versatz 2 vor.    The interaction of the individual cylinders in the crank mechanism is explained using an 8-cylinder version of the internal combustion engine. According to FIG. 1, the cylinders Z1 and Z3 are assigned to the first row R1, the cylinders Z2 and Z4 to the third row R3, the cylinders Z5 and Z7 to the second row R2 and the cylinders Z6 and Z8 to the fourth row R4.
    A crankshaft 4 of the internal combustion engine has a total of four crankings 5, 6, 7, 8 and is supported in a total of five main bearings 9 of a crankcase 10. To achieve a uniform and comfortable firing order, two cylinders each work on one of the cranks by means of the connecting rods 11 assigned to them, the two conrod bearings 12, 13 of a crank having an offset by a difference angle Δwinkel.
    The cylinders, which are staggered relative to each other by the group offset 3 and are assigned to one of the V-spaces V1 or V2, work on one of the offsets. Thus, the connecting rods 11 of the cylinders Z1 and Z5 with the crank 5, the cylinders Z2 and Z6 with the crank 6, the cylinders Z3 and Z7 with the crank 7 and the cylinders Z4 and Z8 with the crank 8. As can be seen from FIG. 2, on the right, the connecting rods 11 of the cylinders Z1 and Z5 lying in the sectional planes SE1 and SE2 are spaced apart from one another by the offset 3 in the crank 5. Between the connecting rods 11 of cylinders Z5 and Z6 lying in the sectional plane SE2 and SE4 there is the row offset 2, usually referred to as the cylinder spacing.

    Der Kurbeltrieb der Brennkraftmaschine ist geschränkt ausgeführt, das heißt die um den Zylinderwinkel αG1 bzw. αG2 zueinanderstehenden Zylinderachsen ZR1, ZR3 bzw. ZR2, ZR4 schneiden sich nicht mit der Kurbelwellenachse 1. Bezüglich einer die Mittelebene senkrecht entlang der Kurbelwellenachse 1 durchdringenden Querebene QE liegt ein Schnittpunkt SP1 der ersten Gruppe G1 auf der Seite S2 auf der von den Reihen R1 und R3 abgewandten Seite der Querebene QE. Spiegelbildlich bezüglich der Mittelebene ME liegt dazu ein weiterer Schnittpunkt SP2 der zweiten Gruppe G2.
    Aufgrund der Schränkung des Kurbeltriebes fallen die maximalen Strecklagen der Pleuel 11 im oberen bzw. unteren Totpunkt OT bzw. UT nicht mit der jeweiligen Zylinderachse ZR zusammen. Wird der während der Drehung der Kurbelwelle 4 auftretende Kurbelwinkel ϕ in Anlehnung an einen ungeschränkten Kurbeltrieb von einer Parallelen 13 zur Zylinderachse ZR durch die Kurbelwellenachse 1 ausgezählt, so werden OT und UT bei einem Kurbelwinkelversatz von ϕ* erreicht. Aufgrund der Lage der Schnittpunkte SP1 und SP2 bezüglich der Querebene QE auf der von den Gruppen G1 bzw. G2 abgewandten Seite stellt sich eine positive oder negative Schränkung ein, so daß der untere Totpunkt UT dem oberen Totpunkt OT nach mehr oder weniger als 180° Kurbelwinkel ϕ folgt.    The crank mechanism of the internal combustion engine is designed to be limited, that is to say the cylinder axes ZR1, ZR3 or ZR2, ZR4, which are at an angle to one another by the cylinder angle αG1 or αG2, do not intersect with the crankshaft axis 1 Intersection SP1 of the first group G1 on the side S2 on the side of the transverse plane QE facing away from the rows R1 and R3. For this purpose, another intersection point SP2 of the second group G2 lies in mirror image with respect to the center plane ME.
    Because of the cranking of the crank mechanism, the maximum extension positions of the connecting rods 11 at top and bottom dead center OT and UT do not coincide with the respective cylinder axis ZR. If the crank angle ϕ occurring during the rotation of the crankshaft 4 is counted by the crankshaft axis 1, based on an unrestricted crank drive from a parallel 13 to the cylinder axis ZR, then TDC and TDC are achieved with a crank angle offset of ϕ *. Due to the position of the intersection points SP1 and SP2 with respect to the transverse plane QE on the side facing away from the groups G1 and G2, a positive or negative setpoint is set, so that the bottom dead center UT and the top dead center OT after more or less than 180 ° crank angle ϕ follows.

    Die gewählte Schränkung ermöglicht ein bauraumoptimierendes Zusammenrücken der Zylinder innerhalb der Gruppen G1 und G2, so daß die jeweiligen Zylinder dieser Gruppen G1 und G2 in einem gemeinsamen Zylinderblock 15 bzw. 16 zusammengegossen werden können. Diese sind jeweils von einem den beiden Zylinderreihen einer Gruppe gemeinsamen Zylinderkopf 17 bzw. 18 überdeckt.The selected setting enables the space to be moved closer together Cylinders within groups G1 and G2, so that the respective cylinders of these groups G1 and G2 are cast together in a common cylinder block 15 and 16, respectively can. These are common to one of the two rows of cylinders in a group Cylinder head 17 or 18 covered.

    Das Zusammenspiel der zuvor erläuterten 8-zylindrigen Anordnung sei kurz anhand eines Zahlenbeispieles erläutert. Die Gabelwinkel δ1 und δ2 betragen 72°, die Zylinderwinkel αG1 und αG2 jeweils 15°. Aufgrund der symmetrischen Anordnung zu der Mittelebene ME stellt sich bezüglich der Winkelhalbierenden 19 der Zylinderwinkel αG1 und αG2 ebenfalls der Gabelwinkel δ1 bzw. δ2 ein. Wegen der in zwei Ebenen liegenden vier Kröpfungen 5 bis 8 stellt sich eine Zündfolge zwischen den einzelnen Zylindern im Abstand von 90° Kurbelwinkel ϕ ein. Bei einer gewählten Zündfolge in der Reihenfolge Z1-Z5-Z4-Z8-Z6-Z3-Z7-Z2, stellen sich die in dem Kurbelstern 20 gemäß Figur 2, links, anhand von den Zylindern Z1 bis Z8 zugeordneten Pfeilen P1 bis P8, gezeigten Lagen der Zündzeitpunkte ein. Während zwischen Zylinder Z1 und Z5, welche auf die eine gemeinsame Kröpfung 5 arbeiten, mit 90° ein harmonischer Zündabstand gegeben wäre, stellt sich aufgrund des Gabelwinkels δ von 72° ein Differenzwinkel von Δϕ von 18° ein, wobei in diesem Falle beim Zünden des Zylinders Z1 im oberen Totpunkt OT der Zylinder Z5 um den Differenzwinkel Δϕ von 18° nacheilt. Für den in der Zündfolge auf den Zylinder 5 folgenden Zylinder Z4 stellt sich infolge des gewälten Gabelwinkels δ, des Zylinderwinkels αG und des Kurbelwinkelversatzes ϕ* ein Kurbelwinkel ϕ von etwa 140° ein. Zum Zündzeitpunkt des Zylinders Z4 eilt der auf der gleichen Kröpfung 8 arbeitende Zylinder Z8 wiederum um den Differenzwinkel Δϕ von 18° nach.The interaction of the previously explained 8-cylinder arrangement is briefly based on one Numerical example explained. The fork angles δ1 and δ2 are 72 °, the cylinder angles αG1 and αG2 each 15 °. Due to the symmetrical arrangement to the central plane ME the cylinder angles αG1 and αG2 also arise with respect to the bisector 19 the fork angle δ1 or δ2. Because of the four offsets 5 to lying on two levels 8 there is an ignition sequence between the individual cylinders at a crank angle of 90 ° ϕ a. With a selected firing order in the order Z1-Z5-Z4-Z8-Z6-Z3-Z7-Z2, 2 in the crank star 20 according to FIG. 2, based on the cylinders Z1 to Z8 assigned arrows P1 to P8, shown positions of the ignition timing. While between cylinders Z1 and Z5, which work on a common crank 5 with 90 ° there would be a harmonic firing interval due to the fork angle δ of 72 ° a difference angle of Δϕ of 18 °, in which case when the Cylinder Z1 at top dead center TDC of cylinder Z5 by the difference angle Δϕ of 18 ° lags behind. For cylinder Z4 following cylinder 5 in the firing order, this results in the selected fork angle δ, the cylinder angle αG and the crank angle offset ϕ * Crank angle ϕ of about 140 °. At the time of ignition of cylinder Z4, the one on the same crank 8 working cylinders Z8 in turn by the difference angle Δϕ of 18 ° after.

    Alternativ kann bei einer 10-zylindrigen Anordnung auf den Versatz innerhalb der einzelnen Kröpfungen 5 bis 8 verzichtet werden. Hierbei sind den Reihen R3 und R4 jeweils drei Zylinder zugeordnet, während die Reihen R1 und R2 jeweils zwei Zylinder tragen. Während hierbei die zuvor beschriebene spiegelbildliche Anordnung der erwähnten Winkellagen zu der Mittelebene ME erhalten bleibt, ist die Anordnung der Reihen nicht spiegelbildlich, da auf die auf der Seite S1 liegende dreizylindrige Reihe R3 auf der Seite S2 zunächst eine zweizylindrige Reihe R2 folgt. Alternatively, in the case of a 10-cylinder arrangement, the offset within the individual Cranks 5 to 8 are dispensed with. The rows R3 and R4 are three each Cylinder assigned, while the rows R1 and R2 each carry two cylinders. While here the previously described mirror-image arrangement of the angular positions mentioned the middle plane ME is preserved, the arrangement of the rows is not a mirror image, because on the three-cylinder row R3 lying on the side S1 initially has one on the side S2 two-cylinder row R2 follows.

    Unter der Annahme, daß es sich auch hierbei um eine 4-Takt-Brennkraftmaschine handelt, ist bei einem Gabelwinkel von 72° der Versatz innerhalb der insgesamt 5 Kröpfungen entbehrlich. Zur Erzielung eines gleichmäßigen Zündabstandes von 72° Kurbelwinkel ϕ liegen die 5 Kröpfungen in insgesamt 5 Ebenen.Assuming that this is also a 4-stroke internal combustion engine, With a fork angle of 72 ° there is no need to offset within the total of 5 crankings. To achieve an even firing interval of 72 ° crank angle ϕ the 5 cranks in a total of 5 levels.

    In einer weiteren Alternative mit einer insgesamt 12-zylindrigen Anordnung stellt sich bei einem Gabelwinkel von 72° eines 4-Takt-Motors eine Zündfolge mit einem Abstand von 60° Kurbelwinkel ϕ ein. Die Kurbelwelle 4 trägt hierbei insgesamt sechs mit einem Versatz um den Differenzwinkel Δϕ versehene Kröpfungen. Unter Annahme des gleichen Gabelwinkels δ von 72° und des Zündabstandes von 60° stellt sich an jeder Kröpfung ein Differenzwinkel Δϕ von 12° ein. Hierbei arbeitet beispielsweise gemäß Figur 1 ein Zylinder Z'1 der ersten Reihe R1 mit dem siebten Zylinder Z'7 der Reihe R2 auf eine Kröpfung, wobei dann nach dem Zünden von Z'1 in OT der Zylinder Z'7 um den Differenzwinkel Δϕ von 12° voreilt.In a further alternative with a total of 12-cylinder arrangement it turns out a fork angle of 72 ° of a 4-stroke engine an ignition sequence with a distance of 60 ° Crank angle ϕ on. The crankshaft 4 transmits a total of six with an offset offsets provided with the difference angle Δϕ. Assuming the same fork angle δ of 72 ° and the ignition distance of 60 ° there is a difference angle Δϕ at each crank of 12 °. Here, for example, according to FIG. 1, a cylinder Z'1 of the first row works R1 with the seventh cylinder Z'7 of the series R2 on a crank, whereby after the Ignition of Z'1 in TDC of cylinder Z'7 leads by the difference angle Δϕ of 12 °.

    Der Kurbelwelle 4 ist abtriebsseitig ein Schwungrad 25 zugeordnet. Benachbart zu diesem ist ein Kettentrieb zum Antrieb von Nockenwellen 27 und 28 der Gruppe G1 und Nockenwellen 29 und 30 der Gruppe G2 angeordnet. Diese betätigen über Nocken 31 und 32 als Hubventile ausgebildete Einlaßventile 33 und Auslaßventile 34 unter Zwischenschaltung von Rollenschlepphebeln 35, wobei jedem Zylinder Z1 bis Z8 vier Hubventile zugeordnet sind.A flywheel 25 is assigned to the crankshaft 4 on the output side. Adjacent to this is a chain drive for driving camshafts 27 and 28 of group G1 and camshafts 29 and 30 of group G2 arranged. These operate via cams 31 and 32 as Lift valves designed intake valves 33 and exhaust valves 34 with the interposition of Roller rocker arms 35, four lift valves being assigned to each cylinder Z1 to Z8.

    Die symmetrische und insgesamt vierreihige Anordnung der Zylinder ermöglicht die Ausbildung von völlig symmetrisch und gleichartig gestalteten Atmungswegen zur Frischluftzufuhr sowie eine symmetrische Anordnung von Abgasleitungen.
    Eine Luftansauganlage zur Beatmung der Brennräume 40 der Brennkraftmaschine ist im wesentlichen symmetrisch zur Mittelebene ME und mit oberhalb der Gruppen G1 und G2 ausgebildeten Sammelvolumina 37 und 38 versehen. Verbrennungsluft wird über Saugrohre 41 aus den erwähnten Sammelvolumina 37, 38 zu Einlaßkanälen 41 geführt, wobei alle Einlaßkanäle 41 einer Gruppe G1 bzw. G2 in je einen Flansch 42 münden, welcher an der Reihe R3 bzw. R2 der Mittelebene ME zugewandt ausgebildet ist. Alle Auslaßkanäle 43 der jeweiligen Gruppe G1 oder G2 sind zu bezüglich der Mittelebene ME außenliegenden Flanschen 44 der Reihen R1 bzw. R4 geführt.    The symmetrical and four-row arrangement of the cylinders enables the formation of completely symmetrical and identical breathing paths for fresh air supply as well as a symmetrical arrangement of exhaust pipes.
    An air intake system for ventilating the combustion chambers 40 of the internal combustion engine is essentially symmetrical to the central plane ME and is provided with collecting volumes 37 and 38 formed above the groups G1 and G2. Combustion air is fed via suction pipes 41 from the above-mentioned collecting volumes 37, 38 to inlet channels 41, all inlet channels 41 of a group G1 or G2 each opening into a flange 42 which is formed on the row R3 or R2 facing the central plane ME. All outlet channels 43 of the respective group G1 or G2 are led to flanges 44 of the rows R1 and R4, which are external to the central plane ME.

    Die Zylinderblöcke 15 und 16 sind einstückig und materialeinheitlich mit dem Kurbelgehäuse 10 ausgebildet, dessen außenliegende Wandungen 45 im Bereich der Kurbelwellenachse 1 über die Querebene QE gezogen sind.The cylinder blocks 15 and 16 are in one piece and of the same material as the crankcase 10 formed, the outer walls 45 in the region of the crankshaft axis 1 are drawn across the transverse plane QE.

    Claims (12)

    1. Reciprocating internal combustion engine having a first and a second row (R1 and R2) of cylinders which are positioned with respect to each other so as to form a V-shape and which are arranged offset along one of the rows (R1, R2) with respect to the cylinders of the other row (R2, R1) in the longitudinal direction of the internal combustion engine, and having two further third and fourth rows (R3 and R4) of cylinders which are positioned with respect to each other so as to form a V-shape and whose one row (R3) is disposed in the installation space (V1) between the first and second row (R1 and R2) and whose other row (R4) is disposed outside the V-space (V1), wherein all of the cylinders (Z1 to Z8) are connected to a common crank shaft (4), characterised in that the cylinder axes (ZR1, ZR2) of the first and second row (R1 and R2) are arranged lying in planes of intersection (SE1, SE2) which extend perpendicular to a middle plane (ME) which receives the crank shaft (4) and which planes of intersection are spaced apart from each other in the direction of the crank shaft axis (1) by a distance (3) equal to the distance at which the groups are offset from each other and the cylinder axes (ZR2, ZR4) of the second and fourth row (R2 and R4) are arranged lying in planes of intersection (SE2, SE4) which extend perpendicular to the middle plane (ME) and which are spaced apart from each other by a distance (2) equal to the distance at which the rows are offset from each other, and the plane of intersection (SE2) which receives the cylinder axes (ZR2) of the second row (R2) extends between the planes of intersection (SE1 and SE3) which receive the cylinder axes (ZR1 and ZR3) of the first and third row (R1 and R3).
    2. Internal combustion engine according to claim 1, characterised in that the distance (2) at which the rows are offset from each other is selected to be greater than the distance (3) at which the groups are offset from each other.
    3. Internal combustion engine according to claim 2, characterised in that the fork angles (δ1 and δ2) which are formed between the first and second row (R1 and R2) and the third and fourth row (R3 and R4) are identical in size and that the V-spaces (V1, V2) which are formed by these fork angles (δ1, δ2) are arranged rotated about a cylinder angle (αG1, αG2) with respect to each other such that the first and third row (R1 and R3) which are positioned with respect to each other at this cylinder angle (αG1) lie in a mirror-symmetrical manner in relation to the second and fourth row (R2 and R4) with respect to the middle plane (ME) of the internal combustion engine.
    4. Internal combustion engine according to claim 3, characterised in that the cylinder axes (ZR1, ZR3 and ZR2, ZR4) of the rows (R1, R3 and R2, R4) which are each arranged on one side (S1 and S2) of the middle plane (ME) intersect, wherein the points of intersection (SP1 and SP2), in relation to a transverse plane (QE) extending perpendicular to the middle plane (ME) through the crank shaft axis (1), lie on the side of this transverse plane (QE) remote from the rows (R1 to R4) and lie on the opposite side (S2 and S1) of the middle plane (ME).
    5. Internal combustion engine according to claim 3 or 4, characterised in that the cylinder number is an integer-multiple of the number of rows of cylinders and two cylinders (Z1 and Z5), which are offset with respect to each other by the value of the fork angle (δ1, δ2), of the first and second row (R1 and R2) or cylinders (Z2 and Z6) of the third and fourth row (R3 and R4) are connected to a common, offset angle bend (5, 6) of the crank shaft (4).
    6. Internal combustion engine according to claim 3 or 4, characterised in that at least two (R3, R4) of the rows have an identical, greater number of cylinders than the two other rows (R1, R2).
    7. Internal combustion engine, according to claim 6, characterised in that the rows (R3, R4) having the greater number of said cylinders are offset with respect to each other by the value of the fork angle (δ1, δ2).
    8. Internal combustion engine according to any one or several of the preceding claims 1 to 7, characterised in that the cylinder angle (αG1, αG2) formed between the first and the third row and the second and fourth row (R1 and R3 or R2 and R4) respectively is selected to be comparatively small, so that the cylinders (Z1 to Z4), which are combined to form a first group (G1), of the rows (R1 and R3) are combined to form a single-piece cylinder block (15) and the other cylinders (Z5 to Z8) are combined to form an identical cylinder block (16) of a second group (G2).
    9. Internal combustion engine according to any one or several of the preceding claims 1 to 8, characterised in that the fork angle (δ1, δ2), which is formed between the first and second row (R1 and R2) and between the third and fourth row (R3 and R4) respectively, amounts to between 60° and 90°, preferably 72°.
    10. Internal combustion engine according to claim 9, characterised in that the cylinder angle (αG1, αG2), which occurs between the cylinders of the first row (R1) and the third row (R3) and between the second row (R2) and the fourth row (R4) respectively, amounts to between 10° and 20°, preferably 15°.
    11. Internal combustion engine according to claim 5 or 6, characterised in that the cylinder axes (ZR1, ZR2), which lie spaced apart from each other by the distance (3) at which the groups are offset from each other, operate on a common angle bend (5) of the crank shaft (4).
    12. Internal combustion engine according to claim 5 or 6, characterised in that the cylinder axes (ZR2, ZR4), which are spaced apart from each other by the distance (2) at which the rows are offset from each other, each operate on their own angle bend (5, 6) of the crank shaft (4).
    EP97914224A 1996-04-23 1997-03-12 Reciprocating internal combustion engine Expired - Lifetime EP0895563B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19616030 1996-04-23
    DE19616030 1996-04-23
    PCT/EP1997/001239 WO1997040267A1 (en) 1996-04-23 1997-03-12 Reciprocating internal combustion engine

    Publications (2)

    Publication Number Publication Date
    EP0895563A1 EP0895563A1 (en) 1999-02-10
    EP0895563B1 true EP0895563B1 (en) 1999-11-03

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    Application Number Title Priority Date Filing Date
    EP97914224A Expired - Lifetime EP0895563B1 (en) 1996-04-23 1997-03-12 Reciprocating internal combustion engine

    Country Status (6)

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    EP (1) EP0895563B1 (en)
    JP (1) JP2000508736A (en)
    DE (2) DE59700667D1 (en)
    ES (1) ES2140224T3 (en)
    PT (1) PT895563E (en)
    WO (1) WO1997040267A1 (en)

    Families Citing this family (8)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP1021648A1 (en) * 1998-08-07 2000-07-26 DaimlerChrysler AG Internal combustion engine
    FR2845422B1 (en) * 2002-10-04 2004-12-17 Olivier Lhuillier 4-STROKE INTERNAL COMBUSTION ENGINE WITH "W" DRIVE CHAIN
    DE102004021360B4 (en) * 2004-04-30 2009-03-19 Audi Ag Internal combustion engine with cylinder pairs
    DE102004042765B4 (en) * 2004-09-05 2007-07-19 Clemens Neese Motorcycle with a space and weight-saving engine arrangement
    DE102008047719B4 (en) * 2008-09-18 2011-03-10 Dieter Hartmann-Wirthwein Crank drive for four-cylinder internal combustion engines
    DE102010021613B4 (en) * 2010-05-26 2012-06-21 Horex Gmbh Motorcycle with compact internal combustion engine
    DE102016117251B4 (en) 2016-09-14 2019-08-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Motorcycle with compact reciprocating internal combustion engine
    DE102016015112A1 (en) 2016-12-20 2018-06-21 Deutz Aktiengesellschaft Internal combustion engine with partial piston restriction

    Family Cites Families (4)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    FR490351A (en) * 1917-12-17 1919-04-19 Gaston Mougeotte Valveless explosive engine with fan-type cylinder groups
    US1407336A (en) * 1918-07-15 1922-02-21 Harvey J Sallee Internal-combustion engine
    FR1024825A (en) * 1950-09-22 1953-04-07 Improvements to internal combustion engines
    FR1430302A (en) * 1965-01-20 1966-03-04 Westinghouse Freins & Signaux Improvements made to rotating machines with reciprocating pistons, to balance the secondary inertia forces

    Also Published As

    Publication number Publication date
    JP2000508736A (en) 2000-07-11
    DE19716274A1 (en) 1997-10-30
    ES2140224T3 (en) 2000-02-16
    DE59700667D1 (en) 1999-12-09
    WO1997040267A1 (en) 1997-10-30
    EP0895563A1 (en) 1999-02-10
    DE19716274B4 (en) 2012-05-24
    PT895563E (en) 2000-04-28

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