EP0459428B1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
EP0459428B1
EP0459428B1 EP19910108745 EP91108745A EP0459428B1 EP 0459428 B1 EP0459428 B1 EP 0459428B1 EP 19910108745 EP19910108745 EP 19910108745 EP 91108745 A EP91108745 A EP 91108745A EP 0459428 B1 EP0459428 B1 EP 0459428B1
Authority
EP
European Patent Office
Prior art keywords
crankcase
combustion engine
internal combustion
engine according
bands
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19910108745
Other languages
German (de)
French (fr)
Other versions
EP0459428A1 (en
Inventor
Bruno Spessert
Monika Breuer
Toni Kleinschmidt
Hermann Reddert
Albert Nolte
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Deutz AG
Kloeckner Humboldt Deutz 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
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Application filed by Deutz AG, Kloeckner Humboldt Deutz AG filed Critical Deutz AG
Priority to DE59102470T priority Critical patent/DE59102470D1/en
Publication of EP0459428A1 publication Critical patent/EP0459428A1/en
Application granted granted Critical
Publication of EP0459428B1 publication Critical patent/EP0459428B1/en
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Classifications

    • 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
    • F02F7/0043—Arrangements of mechanical drive elements
    • F02F7/0053—Crankshaft bearings fitted in the crankcase
    • 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
    • F02F7/0002—Cylinder arrangements
    • F02F7/0007—Crankcases of engines with cylinders in line
    • 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
    • F02F7/0065—Shape of casings for other machine parts and purposes, e.g. utilisation purposes, safety
    • F02F7/008—Sound insulation

Definitions

  • the invention relates to an internal combustion engine according to the preamble of claim 1.
  • a generic internal combustion engine is known from DE-OS 38 31 266.
  • the internal combustion engine described in this document is generally rigid and low-noise.
  • a strut system is provided which is attached to the outside of the internal combustion engine.
  • the bearing arrangement for receiving the crankshaft is connected to the crankcase via a solid apron, which has only a small recess.
  • This design has the disadvantage that the internal combustion engine as a whole is very heavy, in particular due to the massive connection of the bearing arrangement to the crankcase.
  • the invention has for its object to provide an internal combustion engine that has a low weight with low noise emissions from the moving parts.
  • This object is achieved in that the tapes are supported by intermediate stiffeners towards the crankcase wall.
  • This design enables a weight reduction compared to the known design, but the noise emitted by the moving parts is low.
  • the stiffeners are designed as cross girders. This embodiment has proven to be favorable in terms of high rigidity and also in terms of low noise emissions.
  • the cross girders advantageously extend from the connection region of the bands with the bearing base body to the opposite crankcase wall running between the bands.
  • the stiffeners can be connected in a central area between the bearing base body and the crankcase on the belts and on the crankcase wall connecting the belts. Both training courses have proven to be favorable in terms of weight and noise emissions.
  • the cross-sectional area of the stiffeners is 0.3 times to 0.7 times the cross-sectional area of the strips.
  • 0.5 times the cross-sectional area has proven to be particularly favorable.
  • the bearing base body and / or the strips are connected to the crankcase bell by means of ribs.
  • This design makes the overall system even stiffer and at the same time enables a further reduction in the thickness of the crankcase bell walls as well as the bearing arrangement as a whole.
  • the ribs together with the bearing base form an at least approximately rectilinear connection plane between the two sides of the crankcase bell.
  • Ribs which contribute particularly to the rigidity can be provided with further ribs which extend to an oil pan flange of the crankcase bell and, if appropriate, are also connected to the belts in the upper region of the crankcase bell.
  • crankcase bell has internal and / or external webs in the region of the connecting points of the ribs.
  • the oil pan flange has a width that is 0.4 times to 0.6 times, preferably 0.5 times, the cylinder bore dimension.
  • 1 has a crankcase block 1 which is composed essentially of a crankcase bell 2 and a cylinder section 3. Bearing arrangements for receiving a crankshaft are fastened in the crankcase bell 2 and are connected to a piston per cylinder unit via a connecting rod. The piston is movable in the cylinder 4.
  • Each bearing arrangement consists of a bearing base body 5 which, together with a bearing cover 7 connected to the bearing base body 5 by screws 6, has a recess 8 for receiving the crankshaft.
  • the bearing base body 5 is connected to the block 1 via two bands 9a and 9b.
  • the straps 9a, 9b extend in an axial extension of the screws 6.
  • the straps 9a, 9b are stiffened towards the block 1 by stiffeners, which are designed as cross girders 10.
  • the crossbeams 10 extend from the connection area of the belts 9a, 9b with the bearing base 5 to the opposite crankcase wall 11 running between the belts 9a, 9b.
  • ribs 12 are also provided, which are approximately in the center of the recess 8 on both sides of the bearing base and Crankcase bell 2 are connected, so that there is an at least approximately straight connection plane.
  • Further ribs 12a extend from the bearing base body 5 to an oil pan flange 13. In contrast to FIG. 1, a further pair of ribs 12b is provided in FIG.
  • the ribs 12 are wedge-shaped and the oil pan flange 13 is made narrower.
  • internal and external webs 14a, 14b are connected to the crankcase bell in the region of the connecting points of the ribs 12.
  • the stiffeners are connected in a central area between the bearing body 5 and the crankcase wall 11 on the belts 9a, 9b and on the crankcase wall 11 connecting the belts 9a, 9b.
  • the ribs 12a extend from the bearing base body 5 to an inwardly widened oil pan flange 13.

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)

Description

Die Erfindung betriffl eine Brennkraftmaschine gemäß Oberbegriff des Patentanspruchs 1.The invention relates to an internal combustion engine according to the preamble of claim 1.

Eine gattungsgemäße Brennkraftmaschine ist aus der DE-OS 38 31 266 bekannt. Die in dieser Schrift beschriebene Brennkraftmaschine ist insgesamt biegesteif und geräuscharm ausgebildet. Dazu ist ein Strebensystem vorgesehen, das außen an die Brennkraftmaschine angesetzt ist. Des weiteren ist die Lageranordnung zur Aufnahme der Kurbelwelle über eine massive Schürze, die nur eine kleine Ausnehmung aufweist, mit dem Kurbelgehäuse verbunden. Diese Ausbildung hat den Nachteil, daß insbesondere durch die massive Anbindung der Lageranordnung an das Kurbelgehäuse die Brennkraftmaschine insgesamt sehr schwer ist.A generic internal combustion engine is known from DE-OS 38 31 266. The internal combustion engine described in this document is generally rigid and low-noise. For this purpose, a strut system is provided which is attached to the outside of the internal combustion engine. Furthermore, the bearing arrangement for receiving the crankshaft is connected to the crankcase via a solid apron, which has only a small recess. This design has the disadvantage that the internal combustion engine as a whole is very heavy, in particular due to the massive connection of the bearing arrangement to the crankcase.

Der Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine bereitzustellen, die bei niedrigen von den bewegten Teilen ausgehenden Geräuschemissionen ein geringes Gewicht hat.The invention has for its object to provide an internal combustion engine that has a low weight with low noise emissions from the moving parts.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die Bänder durch dazwischenliegende Versteifungen zu der Kurbelgehäusewand hin abgestützt sind. Diese Ausbildung ermöglicht eine Gewichtsreduzierung gegenüber der bekannten Ausführung, wobei aber die von den bewegten Teilen ausgehende Geräuschemission niedrig ist.This object is achieved in that the tapes are supported by intermediate stiffeners towards the crankcase wall. This design enables a weight reduction compared to the known design, but the noise emitted by the moving parts is low.

In vorteilhafter Weiterbildung sind die Versteifungen als Kreuzträger ausgebildet. Diese Ausführungsform hat sich hinsichtlich hoher Steifigkeit und auch bezüglich niedriger Geräuschemission als günstig erwiesen.In an advantageous development, the stiffeners are designed as cross girders. This embodiment has proven to be favorable in terms of high rigidity and also in terms of low noise emissions.

Dabei erstrecken sich vorteilhaft die Kreuzträger vom Verbindungsbereich der Bänder mit dem Lagergrundkörper zu der gegenüberliegenden zwischen den Bändern verlaufenden Kurbelgehäusewand. Alternativ können die Versteifungen in einem mittigen Bereich zwischen Lagergrundkörper und Kurbelgehäuse an den Bändern und an der die Bänder verbindenden Kurbelgehäusewand angebunden sein. Beide Ausbildungen haben sich als gewichtsund geräuschemissionsmäßig günstig herausgestellt.In this case, the cross girders advantageously extend from the connection region of the bands with the bearing base body to the opposite crankcase wall running between the bands. Alternatively, the stiffeners can be connected in a central area between the bearing base body and the crankcase on the belts and on the crankcase wall connecting the belts. Both training courses have proven to be favorable in terms of weight and noise emissions.

Die Querschnittsfläche der Versteifungen beträgt in Weiterbildung der Erfindung das 0,3-fache bis 0,7-fache der Querschnittsfläche der Bänder. Dabei hat sich die 0,5-fache Querschnittsfläche als besonders günstig erwiesen.In a further development of the invention, the cross-sectional area of the stiffeners is 0.3 times to 0.7 times the cross-sectional area of the strips. Here, 0.5 times the cross-sectional area has proven to be particularly favorable.

In Weiterbildung der Erfindung ist vorgesehen, daß der Lagergrundkörper und/oder die Bänder mit der Kurbelgehäuseglocke über Rippen verbunden sind. Diese Ausbildung macht das Gesamtsystem noch steifer und ermöglicht gleichzeitig eine weitere Verringerung der Dicken der Kurbelgehäuseglockenwände sowie auch der Lageranordnung insgesamt.In a further development of the invention it is provided that the bearing base body and / or the strips are connected to the crankcase bell by means of ribs. This design makes the overall system even stiffer and at the same time enables a further reduction in the thickness of the crankcase bell walls as well as the bearing arrangement as a whole.

Dabei bilden in vorteilhafter Weiterbildung der Erfindung die Rippen zusammen mit dem Lagergrundkörper eine zumindest angenähert geradlinige Verbindungsebene zwischen den beiden Seiten der Kurbelgehäuseglocke. Ausgehend von dieser besonders zur Steifigkeit beitragenden Rippenanordnung können noch weitere Rippen vorgesehen sein, die sich zu einem Ölwannenflansch der Kurbelgehäuseglocke erstrecken und gegebenenfalls auch im oberen Bereich der Kurbelgehäuseglocke mit den Bändern verbunden sind.In an advantageous development of the invention, the ribs together with the bearing base form an at least approximately rectilinear connection plane between the two sides of the crankcase bell. Starting from this Ribs which contribute particularly to the rigidity can be provided with further ribs which extend to an oil pan flange of the crankcase bell and, if appropriate, are also connected to the belts in the upper region of the crankcase bell.

In Weiterbildung der Erfindung ist vorgesehen, daß die Kurbelgehäuseglocke im Bereich der Anbindestellen der Rippen innenliegende und/oder außenliegende Stege aufweist. Dadurch können in den übrigen Bereichen der Kurbelgehäuseglocke weitere Materialeinsparungen vorgenommen und die Geräuschemission und das Gewicht verringert werden.In a further development of the invention it is provided that the crankcase bell has internal and / or external webs in the region of the connecting points of the ribs. As a result, further material savings can be made in the other areas of the crankcase bell and the noise emission and the weight can be reduced.

Schließlich weist der Ölwannenflansch eine Breite auf, die das 0,4-fache bis 0,6-fach, vorzugsweise das 0,5-fache, des Zylinderbohrungsmaßes beträgt.Finally, the oil pan flange has a width that is 0.4 times to 0.6 times, preferably 0.5 times, the cylinder bore dimension.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der mehrere in der Zeichnung dargestellte Ausführungsformen der Erfindung beschrieben sind.Further advantageous embodiments of the invention can be found in the description of the drawing, in which several embodiments of the invention shown in the drawing are described.

Es zeigen:

Fig.1:
Eine erste Ausführungsform,
Fig.2:
eine Ausführungsform mit besonders angebundener Kurbelgehäuseglockenwand,
Fig.3:
eine Ausführungsform mit zusätzlichem Steg an der Kurbelgehäuseglockenwand und
Fig.4:
eine Ausführungsform mit einer V-förmigen Versteifung.
Show it:
Fig.1:
A first embodiment
Fig. 2:
an embodiment with a specially connected crankcase bell wall,
Fig. 3:
an embodiment with an additional web on the crankcase bell wall and
Fig. 4:
an embodiment with a V-shaped stiffener.

In der folgenden Zeichnungsbeschreibung sind gleiche, bzw. gleich wirkende Teile mit übereinstimmenden Ziffern bezeichnet und im einzelnen nur die unterschiedlichen Details der verschiedenen Ausführungsformen beschrieben. Die Brennkraftmaschine gemäß Fig. 1 weist einen Kurbelgehäuseblock 1 auf, der sich im wesentlichen aus einer Kurbelgehäuseglocke 2 und einem Zylinderabschnitt 3 zusammensetzt. In der Kurbelgehäuseglocke 2 sind Lageranordnungen zur Aufnahme einer Kurbelwelle befestigt, die je Zylindereinheit über ein Pleuel mit einem Kolben verbunden ist. Dabei ist der Kolben in dem Zylinder 4 bewegbar. Jede Lageranordnung besteht aus einem Lagergrundkörper 5, der zusammen mit einem mit dem Lagergrundkörper 5 über Schrauben 6 verbundenen Lagerdeckel 7 eine Ausnehmung 8 zur Aufnahme der Kurbelwelle aufweist. Der Lagergrundkörper 5 ist über zwei Bänder 9a und 9b mit dem Block 1 verbunden. Dabei erstrecken sich die Bänder 9a, 9b in axialer Verlängerung der Schrauben 6. Weiterhin sind die Bänder 9a, 9b durch Versteifungen, die als Kreuzträger 10 ausgebildet sind, zum Block 1 hin versteift. Dabei erstrecken sich die Kreuzträger 10 vom Verbindungsbereich der Bänder 9a, 9b mit dem Lagergrundkörper 5 zu der gegenüberliegenden zwischen den Bändern 9a, 9b verlaufenden Kurbelgehäusewand 11. Weiterhin sind noch Rippen 12 vorgesehen, die etwa mittig zu der Ausnehmung 8 beidseitig an dem Lagergrundkörper und der Kurbelgehäuseglocke 2 angebunden sind, so daß sich eine zumindest angenähernd geradlinige Verbindungsebene ergibt. Weitere Rippen 12a erstrecken sich von dem Lagergrundkörper 5 zu einem Ölwannenflansch 13. Im Unterschied zur Fig.1 ist bei Fig.2 ein weiteres Rippenpaar 12b vorgesehen, das an die Bänder 9a, 9b und der Kurbelgehäuseglocke 2 angebunden sind. Weiterhin sind die Rippen 12 keilförmig ausgebildet und der Ölwannenflansch 13 schmäler ausgeführt.In the following description of the drawings, the same or equivalent parts are designated by corresponding numbers and only the different details of the various embodiments are described in detail. 1 has a crankcase block 1 which is composed essentially of a crankcase bell 2 and a cylinder section 3. Bearing arrangements for receiving a crankshaft are fastened in the crankcase bell 2 and are connected to a piston per cylinder unit via a connecting rod. The piston is movable in the cylinder 4. Each bearing arrangement consists of a bearing base body 5 which, together with a bearing cover 7 connected to the bearing base body 5 by screws 6, has a recess 8 for receiving the crankshaft. The bearing base body 5 is connected to the block 1 via two bands 9a and 9b. The straps 9a, 9b extend in an axial extension of the screws 6. Furthermore, the straps 9a, 9b are stiffened towards the block 1 by stiffeners, which are designed as cross girders 10. The crossbeams 10 extend from the connection area of the belts 9a, 9b with the bearing base 5 to the opposite crankcase wall 11 running between the belts 9a, 9b. Furthermore, ribs 12 are also provided, which are approximately in the center of the recess 8 on both sides of the bearing base and Crankcase bell 2 are connected, so that there is an at least approximately straight connection plane. Further ribs 12a extend from the bearing base body 5 to an oil pan flange 13. In contrast to FIG. 1, a further pair of ribs 12b is provided in FIG. Furthermore, the ribs 12 are wedge-shaped and the oil pan flange 13 is made narrower.

Bei der Ausführung nach Fig.3 sind an der Kurbelgehäuseglocke im Bereich der Anbindestellen der Rippen 12 innen- und außenliegende Stege 14a, 14b angebunden. Bei der Ausführung nach Fig.4 sind die Versteifungen in einem mittigen Bereich zwischen Lagergrundkörper 5 und Kurbelgehäusewand 11 an den Bändern 9a, 9b und an der die Bänder 9a, 9b verbindenden Kurbelgehäusewand 11 angebunden. Die Rippen 12a erstrecken sich bei dieser Ausführung von dem Lagergrundkörper 5 zu einem nach innen erweiterten Ölwannenflansch 13.In the embodiment according to FIG. 3, internal and external webs 14a, 14b are connected to the crankcase bell in the region of the connecting points of the ribs 12. In the 4, the stiffeners are connected in a central area between the bearing body 5 and the crankcase wall 11 on the belts 9a, 9b and on the crankcase wall 11 connecting the belts 9a, 9b. In this embodiment, the ribs 12a extend from the bearing base body 5 to an inwardly widened oil pan flange 13.

Claims (10)

  1. An internal combustion engine with a crankcase block having a cylinder region and a crankcase bell housing (2), the said crankcase block being provided with bearing arrangements to accommodate a crankshaft which is connected, for each cylinder unit, via a connecting rod to a piston which is movable within a respective cylinder, the cylinders being covered by a cylinder head, wherein each bearing arrangement is provided with a main bearing body (5) which is connected in one piece with the crankcase via a skirt, the said main bearing body, together with a bearing cap (7) screwed or bolted thereto, being provided with a recess to accommodate the crankshaft, and the skirt being provided with bands in axial extension of the screws or bolts of the bearing cap (7), which bands extend from the main bearing body to a crankcase wall (11),
    characterised in that the bands (9a, 9b) are supported by the crankcase wall (11) through interposed reinforcements.
  2. An internal combustion engine according to claim 1,
    characterised in that the reinforcements are in the form of cruciform supports (10).
  3. An internal combustion engine according to claim 2,
    characterised in that the cruciform supports (10) extend from the region of connection of the bands (9a, 9b) with the main bearing body (5) to the opposing crankcase wall (11) extending between the bands (9a, 9b).
  4. An internal combustion engine according to either claim 1 or 2,
    characterised in that the reinforcements are connected in a central region between the main bearing body (5) and the crankcase and the crankcase wall (11) connecting the bands (9a, 9b).
  5. An internal combustion engine according to any one of claims 1 to 4,
    characterised in that the cross-sectional area of the reinforcements is between 30 per cent and 70 per cent of the cross-sectional area of the bands (9a, 9b).
  6. An internal combustion engine according to any one of claims 1 to 5,
    characterised in that the main bearing body (5) and/or the bands (9a, 9b) are connected to the crankcase bell housing (2) via ribs (12, 12a, 12b).
  7. An internal combustion engine according to claim 6,
    characterised in that the ribs (12), together with the main bearing body (5), form at least an approximately rectilinear connection between opposing sides of the crankcase.
  8. An internal combustion engine according to either claim 6 or 7,
    characterised in that at least approximately straight ribs (12, 12a, 12b) extend on both sides of the main bearing body (5) from the cylinder region via the main main bearing body (5) to an oil-sump flange (13) of the crankcase bell housing (2).
  9. An internal combustion engine according to any one of claims 6 to 8,
    characterised in that the crankcase bell housing (2) is provided with inner and/or outer webs (14) in the region of the points of connection of the ribs (12, 12a, 12b).
  10. An internal combustion engine according to either claim 8 or 9,
    characterised in that the oil-sump flange (13) has a width which is between 40 to 60 per cent of the cylinder bore dimension.
EP19910108745 1990-05-28 1991-05-28 Internal combustion engine Expired - Lifetime EP0459428B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE59102470T DE59102470D1 (en) 1991-05-28 1991-05-28 Internal combustion engine.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19904017139 DE4017139C2 (en) 1990-05-28 1990-05-28 Internal combustion engine

Publications (2)

Publication Number Publication Date
EP0459428A1 EP0459428A1 (en) 1991-12-04
EP0459428B1 true EP0459428B1 (en) 1994-08-10

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ID=6407336

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EP19910108745 Expired - Lifetime EP0459428B1 (en) 1990-05-28 1991-05-28 Internal combustion engine

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DE (1) DE4017139C2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4223717C2 (en) * 1992-07-18 2001-09-27 Deutz Ag Noise-optimized crankcase
DE9319054U1 (en) * 1993-12-11 1995-04-13 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Piston machine, in particular piston internal combustion engine with stiffened engine block
DE9319055U1 (en) * 1993-12-11 1995-04-13 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Piston machine, in particular piston internal combustion engine with stiffened engine block by means of interrupted ribs
DE19628110C1 (en) * 1996-07-12 1997-10-02 Daimler Benz Ag Crankcase for reciprocating internal combustion engine
EP2228530A1 (en) 2009-03-13 2010-09-15 Ford Global Technologies, LLC Crankcase for a piston engine
CN106438088A (en) * 2016-11-28 2017-02-22 江苏四达动力机械集团有限公司 Reinforcing structure for cylinder block

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190904888A (en) * 1909-02-27 1910-02-24 Gustavus Green Improvements in the Construction of Light Engines.
FR587093A (en) * 1923-10-12 1925-04-10 Rolls Royce Improvements to the housings of the bearings supporting the engine crankshafts
US2752896A (en) * 1952-01-23 1956-07-03 Krauss Maffei Ag Crankcases, particularly for v-type diesel engines
GB1063082A (en) * 1963-02-06 1967-03-30 Ruston & Hornsby Ltd Frame structure for a reciprocating piston engine or machine
FR1429847A (en) * 1965-04-09 1966-02-25 British Aluminium Co Ltd Improvements to internal combustion engines
GB1541421A (en) * 1975-04-28 1979-02-28 Nat Res Dev Structure of reciprocating internal combustion engines
AT398608B (en) * 1987-09-22 1995-01-25 Avl Verbrennungskraft Messtech CRANKCASE

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Publication number Publication date
EP0459428A1 (en) 1991-12-04
DE4017139A1 (en) 1991-12-05
DE4017139C2 (en) 1999-04-15

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