EP0895563A1 - Moteur alternatif a combustion interne - Google Patents

Moteur alternatif a combustion interne

Info

Publication number
EP0895563A1
EP0895563A1 EP97914224A EP97914224A EP0895563A1 EP 0895563 A1 EP0895563 A1 EP 0895563A1 EP 97914224 A EP97914224 A EP 97914224A EP 97914224 A EP97914224 A EP 97914224A EP 0895563 A1 EP0895563 A1 EP 0895563A1
Authority
EP
European Patent Office
Prior art keywords
rows
cylinders
row
internal combustion
combustion engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP97914224A
Other languages
German (de)
English (en)
Other versions
EP0895563B1 (fr
Inventor
Hermann Deutsch
Frank Metzner
Frank Meyer-Hessing
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
Original Assignee
Volkswagen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP0895563A1 publication Critical patent/EP0895563A1/fr
Application granted granted Critical
Publication of EP0895563B1 publication Critical patent/EP0895563B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02B75/224—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 piston internal combustion engine having a plurality of rows of cylinders along two rows at an angle to one another according to the preamble of patent claim 1
  • 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 closed crank crank leads to a further shortening of the engine.
  • 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 Stuttgart, page 509.
  • a compact arrangement is achieved here by arranging two 8-cylinder drums one above the other Boxer internal combustion engines achieved These each work on their own crankshaft, which, coupled to one another, operate a single-shaft output.
  • the two opposite, 4-cylinder rows have no longitudinal offset from each other since the two connecting rods from opposite cylinders through the use of a connecting rod on a common crank pin Crankshaft work
  • a further compact arrangement of several cylinders of an internal combustion engine in a W shape is known from DE-Z Sportauto, March 1988, No. 3, pages 90 ff.
  • This comparatively wide, but short cylinder arrangement has three 4-cylinder rows of 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 a bisector.
  • the three rows have a longitudinal offset relative to one another, since three cylinders each work with their connecting rods lying next to one another on a common crank pin of the crankshaft.
  • the invention is based on the object of developing a generic reciprocating internal combustion engine with a plurality of cylinders which are at an angle to one another and have a longitudinal offset from one another in such a way that a compact arrangement of a comparatively large number of cylinders is made possible by taking up as little installation space as possible.
  • a proper supply of fresh air or the discharge of the exhaust gases as well as a perfect drive of the gas exchange valves providing the gas exchange are to be ensured.
  • 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.
  • a suitable choice of the angles lying between the individual rows it is possible in this way to achieve a compact arrangement of the cylinders, whereby 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.
  • 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.
  • the additional, third and fourth rows have a longitudinal offset from one another and from the first two rows of cylinders.
  • uniform connecting rods can be used for all cylinders while avoiding comparatively complicated and expensive fork connecting rods.
  • the fork angle formed between the first and second row of cylinders and that between the third and fourth row of cylinders is identical in each case and that the V-spaces formed by this fork angle are rotated relative to one another by a certain cylinder angle chosen so that the first and third or second and fourth rows at this angle to each other are mirror-symmetrical with respect to the other two rows to a central plane of the internal combustion engine receiving the crankshaft. Assuming a perpendicular central plane, V is thus obtained on both sides of this plane Shaped rows of cylinders arranged with respect to one another, the cylinder angle within these V-shaped rows being chosen to be comparatively small
  • crank mechanism of this internal combustion engine is designed to be locked, that is to say the cylinder axes of the two rows on one side of the central plane intersect when the central plane is arranged vertically below this and on the opposite side further shortening of the internal combustion engine is possible by pushing the cylinders assigned to the two rows into each other
  • crank star with 4 crankings resulting from the image of the crankshaft can be provided, each crank having two offset bearings for connecting rods this common, offset cranking each work the connecting rods of two cylinders of the first and third or second and fourth rows which are offset by the fork angle
  • two of the cylinder rows each have three cylinders and the other two have two cylinders
  • the rows with the larger number of cylinders are offset from one another by the fork angle
  • the rows lying on both sides of the central plane and offset by the cylinder angle from one another are each combined to form a coherent cylinder block which can be covered by a cylinder head common to these two rows
  • the two combined cylinder rows can be designed identically on each side of the central plane, which means that further advantageous effects in terms of component expenditure, assembly, etc. can be achieved.
  • Figure 1 is a schematic plan view of an internal combustion engine according to the invention
  • Figure 2 is a schematic side view of Figure 1 of the crank mechanism
  • Figure 3 shows a cross section through an internal combustion engine.
  • 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 arranged, which receives a crankshaft axis 1.
  • the row R1 assigned to the side S1 and the row R2 assigned to the side S2 are at a fork angle 57 in a V-shape to one another and thus define a first V-space VI between them
  • the two further cylinder rows R3 and R4 are assigned to the sides S1 and S2 and are at a fork angle 52, defining another V-space V2, to one another.
  • the third row R3 is thus in the first V-space VI, while the fourth row R4 is arranged outside 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 in turn being at a V-shaped cylinder angle ⁇ G1.
  • the size of the fork angles 57 and 52 is chosen identically, 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 or ZR2 and ZR4 have an identical row offset 2 to one another along crankshaft axis 1.
  • 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 ⁇ .
  • 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 mutually spaced about 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.
  • the selected setting enables the cylinders within the groups G1 and G2 to be moved closer together so that the respective cylinders of these groups G1 and G2 can be cast together in a common cylinder block 15 and 16, respectively. These are each covered by a cylinder head 17 or 18 common to the two cylinder rows of a group.
  • the interaction of the previously explained 8-cylinder arrangement will be briefly explained using a numerical example.
  • the fork angles 81 and 82 are 72 °, the cylinder angles ⁇ G1 and ⁇ G2 each 15 °. Because of the symmetrical arrangement with respect to the center plane ME, the fork angle 57 and 52 is also established with respect to the bisector 19 of the cylinder angles ⁇ G1 and ⁇ G2. Because of the four crankings 5 to 8 lying in two planes, an ignition sequence between the individual cylinders occurs at a distance of 90 ° crank angle ⁇ .
  • a crank angle ⁇ of approximately 140 ° is established as a result of the selected fork angle 5, the cylinder angle ⁇ G and the crank angle offset ⁇ *.
  • the cylinder Z8 working on the same offset 8 again lags by the difference angle ⁇ of 18 °.
  • the offset within the individual crankings 5 to 8 can be dispensed with.
  • the rows R3 and R4 are each assigned three cylinders, while the rows R1 and R2 each carry two cylinders. While the previously described mirror-image arrangement of the mentioned angular positions with respect to the center plane ME is retained, the arrangement of the rows is not mirror-image, since the three-cylinder row R3 lying on the side S1 is first followed by a two-cylinder row R2 on the side S2. 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 5 crankings. In order to achieve an even firing interval of 72 ° crank angle ⁇ , the 5 crankings are in a total of 5 levels.
  • an ignition sequence with a crank angle ⁇ of 60 ° occurs at a fork angle of 72 ° of a 4-stroke engine.
  • the crankshaft 4 carries a total of six offsets provided with an offset by the difference angle ⁇ .
  • a differential angle ⁇ of 12 ° is established at each crank.
  • a cylinder Z'1 of the first row R1 works with a seventh cylinder Z'7 of the row R2 on a crank, whereby after the ignition of Z'1 in TDC, the cylinder Z'7 by the difference angle ⁇ of Leading 12 °.
  • 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. These operate via cams 31 and 32 designed as lift valves inlet valves 33 and outlet valves 34 with the interposition of roller rocker arms 35, four lift valves being assigned to each cylinder Z1 to Z8.
  • the symmetrical and four-row arrangement of the cylinders enables the formation of completely symmetrical and similarly designed breathing paths for supplying fresh air and 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.
  • the cylinder blocks 15 and 16 are formed in one piece and with the same material as the crankcase 10, the outer walls 45 of which are drawn in the region of the crankshaft axis 1 across the transverse plane QE.

Landscapes

  • 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)

Abstract

Dans le but d'obtenir une configuration compacte d'un nombre de cylindres (Z1-Z8) relativement important, l'invention propose que deux rangées de cylindre (R1, R2) soient disposées l'une par rapport à l'autre de manière à former un V, une troisième rangée (R3) étant situé entre les rangées R1 et R2, une quatrième rangée (R4) étant disposée à l'extérieur de l'espace en V entre les rangées R1 et R2, les troisième et quatrième rangées (R3, R4), formant également un V entre elles, et tous les cylindres (Z1-Z8) du moteur à combustion interne agissant sur un seul et même vilebrequin.
EP97914224A 1996-04-23 1997-03-12 Moteur alternatif a combustion interne Expired - Lifetime EP0895563B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19616030 1996-04-23
DE19616030 1996-04-23
PCT/EP1997/001239 WO1997040267A1 (fr) 1996-04-23 1997-03-12 Moteur alternatif a combustion interne

Publications (2)

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

Family

ID=7792106

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914224A Expired - Lifetime EP0895563B1 (fr) 1996-04-23 1997-03-12 Moteur alternatif a combustion interne

Country Status (6)

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

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000008324A1 (fr) * 1998-08-07 2000-02-17 Daimlerchrysler Ag Moteur a combustion interne
FR2845422B1 (fr) * 2002-10-04 2004-12-17 Olivier Lhuillier Moteur a combustion interne a 4 temps a chaine cinematique en"w"
DE102004021360B4 (de) * 2004-04-30 2009-03-19 Audi Ag Brennkraftmaschine mit Zylinderpaaren
DE102004042765B4 (de) * 2004-09-05 2007-07-19 Clemens Neese Kraftrad mit einer platz- und gewichtsparenden Motoranordnung
DE102008047719B4 (de) * 2008-09-18 2011-03-10 Dieter Hartmann-Wirthwein Kurbeltrieb für Vierzylinderverbrennungsmotoren
DE102010021613B4 (de) * 2010-05-26 2012-06-21 Horex Gmbh Kraftrad mit kompakter Verbrennungskraftmaschine
DE102016117251B4 (de) 2016-09-14 2019-08-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Kraftrad mit kompakter Hubkolbenbrennkraftmaschine
DE102016015112A1 (de) 2016-12-20 2018-06-21 Deutz Aktiengesellschaft Brennkraftmaschine mit teilweiser Kolbenschränkung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR490351A (fr) * 1917-12-17 1919-04-19 Gaston Mougeotte Moteur à explosions sans soupapes, à groupes de cylindres en éventail
US1407336A (en) * 1918-07-15 1922-02-21 Harvey J Sallee Internal-combustion engine
FR1024825A (fr) * 1950-09-22 1953-04-07 Perfectionnements apportés aux moteurs à combustion interne
FR1430302A (fr) * 1965-01-20 1966-03-04 Westinghouse Freins & Signaux Perfectionnements apportés aux machines tournantes à pistons alternatifs, pour équilibrer les forces d'inertie secondaires

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9740267A1 *

Also Published As

Publication number Publication date
EP0895563B1 (fr) 1999-11-03
PT895563E (pt) 2000-04-28
DE19716274B4 (de) 2012-05-24
DE59700667D1 (de) 1999-12-09
DE19716274A1 (de) 1997-10-30
JP2000508736A (ja) 2000-07-11
WO1997040267A1 (fr) 1997-10-30
ES2140224T3 (es) 2000-02-16

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