EP0223248A2 - Multicylinder reciprocating-piston machine, in particular internal-combustion engine - Google Patents

Multicylinder reciprocating-piston machine, in particular internal-combustion engine Download PDF

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Publication number
EP0223248A2
EP0223248A2 EP86116066A EP86116066A EP0223248A2 EP 0223248 A2 EP0223248 A2 EP 0223248A2 EP 86116066 A EP86116066 A EP 86116066A EP 86116066 A EP86116066 A EP 86116066A EP 0223248 A2 EP0223248 A2 EP 0223248A2
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EP
European Patent Office
Prior art keywords
crankshaft
housing
gear
arrangement according
camshaft
Prior art date
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Granted
Application number
EP86116066A
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German (de)
French (fr)
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EP0223248A3 (en
EP0223248B1 (en
Inventor
Josef Fritzenwenger
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of EP0223248A2 publication Critical patent/EP0223248A2/en
Publication of EP0223248A3 publication Critical patent/EP0223248A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F02B75/243—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "boxer" type, e.g. all connecting rods attached to separate crankshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • 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
    • F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
    • F02B61/02—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving cycles
    • 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
    • F02F7/0058—Longitudinally or transversely separable crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/026—Gear drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L2003/25—Valve configurations in relation to engine
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the invention relates to an arrangement of shafts and units in multi-cylinder reciprocating piston machines with separate gas exchange control devices, in particular internal combustion engines according to the features of the preamble of the independent claim.
  • the invention has for its object to develop a generic arrangement of shafts and assemblies in a multi-cylinder reciprocating machine so that with a simple structure for a low weight, the production costs are reduced by many rectified processing directions for different function groups and by the possibility of mounting large function groups.
  • the reduction gear can simultaneously drive a camshaft that is aligned with the transmission input shaft and is preferably arranged in the installation space facing away from the transmission input shaft.
  • This provides a structure that can be separated perfectly according to the functional groups of reciprocating piston machine and gear unit.
  • This arrangement also offers the advantage of arranging the shafts of the respective functional unit at a relatively small, parallel distance, as a result of which an overall compact construction is achieved.
  • the arrangement according to the invention enables the use of the free end regions for the arrangement of additional units in the shafts of the reciprocating piston engine, as described in more detail in claim 8.
  • a particularly simple construction of a multi-cylinder reciprocating piston engine with an integrated transmission is achieved for an internal combustion engine with opposing cylinders or cylinder rows.
  • the position of the parting plane in the longitudinal extension of the reciprocating piston machine combined with the shaft arrangement according to the invention makes it possible in a further advantageous embodiment according to claim 3 to form a boxer engine or a V-engine and an integrated gearbox with two housing halves which can be connected in the parting plane.
  • a compact structure is thus achieved, with a substantial part of the mechanics of the reciprocating piston machine and of the transmission being accommodated in only two housing halves.
  • the housing halves thus enclosing the mechanics of two different functional groups are also advantageous for a rigid construction due to their one-piece construction. These one-piece housing halves also result in a further weight reduction in a cast-through design with a rigid construction.
  • the arrangement according to the invention also makes it possible, according to a partial feature of claim 4, at the junction of the functional group reciprocating piston engine with the functional group Gearbox to combine the reduction gearbox with the coupling at the input of the gearbox input shaft into a separate function group.
  • a transverse wall can be provided in the two-part housing for the boxer engine between the first and second and between the second and third functional groups, which results in a particularly rigid design in the connection area between the machine housing and the transmission housing.
  • This configuration also makes it possible to close off the housing common to the reciprocating piston machine and the gear unit at both ends by detachable covers, whereby the further units arranged on the free end regions of the camshaft and crankshaft are accessible.
  • the reduction gear is formed from a gear meshing with a pinion of the crankshaft to achieve a compact structure according to claim 6, which carries a basket of a wet clutch according to a further feature of claim 5.
  • a wet clutch spaces to be sealed against one another are advantageously avoided, so that a common oil sump can also be formed for all three functional groups “reciprocating piston engine”, “reduction gear and clutch” and “gear unit”.
  • the wheel of the reduction gear is equipped with a torsional vibration damper and with a backlash compensation device. This eliminates the need for a separate damper on the transmission input shaft, which makes it easier to design.
  • the crankshaft cooperates according to claim 7 at the pinion end with a starting device which is equipped with a freewheel.
  • housing halves formed in one piece in die-cast design advantageously allows not only the crankshaft with its two ends arranged in one of the housing halves Assemblies, but also to assemble the assembly formed from the camshaft, reduction gear wheel with non-rotatably flanged coupling and transmission input shaft in one operation.
  • a gear unit that can be flanged onto the machine housing is conceivable.
  • the clutch could be designed in such a way that the clutch basket is arranged on the wheel of the reduction gear and the clutch plate pack arranged on the gearbox input shaft is inserted into it during assembly. This configuration is conceivable for a dry clutch.
  • a further machine shaft can also be used with pinions which drive, for example, to drive camshafts arranged in the cylinder head region of the reciprocating engine.
  • a multi-cylinder reciprocating piston machine 1 in the form of a boxer engine comprises a crankshaft 2.
  • a reduction gear 3 is arranged at one end of the crankshaft 2 and is formed from a pinion 4 arranged on the crankshaft 2 and a wheel 5. The reduction is selected so that the wheel 5 rotates at half the speed of the crankshaft 2.
  • the wheel 5 On the side facing the crankshaft 2, the wheel 5 is rotatably connected to a camshaft 6.
  • the wheel 5 On the side facing away from the crankshaft, the wheel 5 has an input shaft 7 of a gear unit 8 in non-rotatable connection.
  • the reduction gear 3 is thus assigned a double function in that it serves on the one hand to drive the camshaft 6 and on the other hand to drive the transmission input shaft 7.
  • crankshaft 2 and the camshaft have mutually parallel axes of rotation 2 ⁇ and 6 ⁇ (FIG. 2), while the axis of rotation 7 ⁇ of the transmission input shaft 7 with the axis of rotation 6 ⁇ Camshaft is aligned.
  • crankshaft 2 and the camshaft 6 with their mutually parallel axes of rotation 2 ⁇ and 6 ⁇ are arranged in a parting plane 9 of a divided machine housing 10 of the boxer engine 1 with cylinders 11 and 12 provided on both sides of the parting plane 9.
  • the gear unit 8 further comprises a housing 13 divided in the parting plane 9 of the machine housing 10.
  • the parts or halves of the gearbox housing 13 and the machine housing 10 which are adjacent on one side of the parting plane 9 are integrally formed with one another in die casting as die cast parts 14 and 15.
  • transverse walls 16 and 17 are arranged so spaced that between the machine housing side
  • the transverse wall 16 and the transverse wall 17 on the gearbox housing side both the reduction gear 3 and one of its wheels 5 with the input shaft 7 of the gear unit 8 are arranged in a rotationally fixed coupling 18.
  • a wet clutch is selected as the clutch 18 to avoid complicated seals for these two functional groups.
  • the reduction gear 3 and the wet clutch 18 form a third functional group between the first functional group of the boxer engine 1 and the second functional group of the gear unit tes 8. All three functional groups are connected to a common oil sump 19, the mirror 20 of which is indicated by a dashed line.
  • the wet clutch 18 cooperates with the wheel 5 in a rotationally fixed manner via a basket 21.
  • the wheel 5 is also equipped with a torsional vibration damper 22.
  • a separate vibration damper for the transmission input shaft 7 can thus be dispensed with.
  • the wheel 5 of the reduction gear 3 meshes directly with the pinion 4 arranged on the crankshaft 2.
  • the wheel 5 can also be equipped with a backlash compensation device (not shown).
  • the boxer engine 1 is closed on the front side by a cover 23 and the gear unit 8 on the output side by a cover 24.
  • the removable cover 23 enables access to a generator 25 arranged in the end region of the crankshaft 2 and to an ignition transmitter 26 and an oil pump 27 which are arranged on the camshaft 6.
  • the crankshaft 2 cooperates at the pinion end with a starter device 28 which includes a starter 29, the pinion 30 of which meshes with a toothed wheel 31.
  • the gear wheel 31 of the starter device 28 is arranged coaxially with the pinion 4 of the reduction gear 3 and is connected to it via a freewheel 32. After starting the boxer engine 1, the freewheel 32 serves as an overrunning freewheel.

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

Abstract

1. A multi-cylinder reciprocating-piston machine, especially an internal combustion engine, - with a crankshaft (2) and a cam shaft (6) driven thereby to actuate gas-change valves, - wherein the crankshaft and the cam shaft are arranged with their axes of rotation in a joint plane (9) of a longitudinally-divided machine housing (10) with cylinders (11, 12) provided on both sides of the joint plane (double-piston engine 1), and - in addition a reduction gear (3) for the driving of the cam shaft (6) by the crankshaft (2) is arranged in an end region of the machine housing (10), - wherein on the other side of a wheel (5) of the reduction gear (3), connected with the cam shaft (6) and rotating with half the rotational speed of the crankshaft (2), a coupling is provided for a further connection which is secure with regard to rotation, characterised in that - the coupling (18) is connected with a primary shaft (7) of a gearing unit (8) which is able to be arranged on the reciprocating-piston machine (1), and - the gearing unit (8) comprises a housing (13) which is divided in the joint plane (9) of the machine housing (10), - wherein each part or, respectively, each half of the gear housing (13) is connected with the adjacent part or respectively the adjacent half of the machine housing (10).

Description

Anordnung von Wellen und Aggregaten bei Mehrzylinder-Hubkolben­maschinen mit gesonderten Gaswechsel-Steuervorrichtungen, insbe­sondere BrennkraftmaschinenArrangement of shafts and units in multi-cylinder reciprocating piston machines with separate gas exchange control devices, in particular internal combustion engines

Die Erfindung bezieht sich auf eine Anordnung von Wellen und Aggregaten bei Mehrzylinder-Hubkolbenmaschinen mit gesonderten Gaswechsel-Steuervorrichtungen, insbesondere Brennkraftmaschinen gemäß den Merkmalen des Oberbegriffes des unabhängigen Patentan­spruches.The invention relates to an arrangement of shafts and units in multi-cylinder reciprocating piston machines with separate gas exchange control devices, in particular internal combustion engines according to the features of the preamble of the independent claim.

Eine derartige Anordnung ist insbesondere bei modernen Brennkraft­maschinen für Zweiradfahrzeuge bekannt. Hierbei wird die Nocken­welle durch ein vom Untersetzungsgetriebe zur Eingangswelle des Getriebeaggregates gesondertes Getriebe angetrieben. Dies führt zu einer Hubkolben-Brennkraftmaschine mit kompliziertem Aufbau, der einerseits ein relativ hohes Gewicht bedingt und andererseits hohe Produktionskosten verursacht.Such an arrangement is known in particular in modern internal combustion engines for two-wheeled vehicles. Here, the camshaft is driven by a gearbox that is separate from the reduction gearbox to the input shaft of the gearbox assembly. This leads to a reciprocating piston internal combustion engine with a complicated structure, which on the one hand requires a relatively high weight and on the other hand causes high production costs.

Der Erfindung liegt die Aufgabe zugrunde, eine gattungsgemäße Anordnung von Wellen und Aggregaten bei einer Mehrzylinder-Hubkol­benmaschine so weiterzubilden, daß bei einfachem Aufbau für ein niedriges Gewicht die Produktionskosten durch viele gleichgerich­tete Bearbeitungsrichtungen für verschiedene Funktionsgruppen sowie durch Montagemöglichkeit großer Funktionsgruppen gesenkt werden.The invention has for its object to develop a generic arrangement of shafts and assemblies in a multi-cylinder reciprocating machine so that with a simple structure for a low weight, the production costs are reduced by many rectified processing directions for different function groups and by the possibility of mounting large function groups.

Diese Aufgabe wird mit den kennzeichnenden Merkmalen des unabhän­gigen Patenanspruches gelöst. Mit der erfindungsgemäßen Anordnung und Auslegung des Untersetzungsgetriebes relativ zur Kurbelwelle kann mit dem Untersetzungsgetriebe zugleich eine mit der Getriebe-­Eingangswelle fluchtende Nockenwelle angetrieben werden, die vorzugsweise in dem von der Getriebe-Eingangswelle abgewandten Bauraum angeordnet ist. Diese gibt einen nach den Funktionsgruppen Hubkolbenmaschine und Getriebeaggregat einwandfrei trennbaren Aufbau. Diese Anordnung bietet weiter den Vorteil, die Wellen der jeweiligen Funktionseinheit in relativ geringem, parallelem Abstand anzuordnen, wodurch ein insgesamt kompakter Aufbau erzielt wird. Weiter ermöglicht die erfindungsgemäße Anordnung bei den Wellen der Hubkolbenmaschine die Nutzung der freien Endbereiche für die Anordnung zusätzlicher Aggregate, wie dies in Anspruch 8 näher beschrieben ist. Schließlich ist mit der Doppelnutzung des Unter­setzungsgetriebes eine erste Gewichtsreduzierung erreicht.This task is solved with the characteristic features of the independent patent claim. With the arrangement according to the invention and the design of the reduction gear relative to the crankshaft, the reduction gear can simultaneously drive a camshaft that is aligned with the transmission input shaft and is preferably arranged in the installation space facing away from the transmission input shaft. This provides a structure that can be separated perfectly according to the functional groups of reciprocating piston machine and gear unit. This arrangement also offers the advantage of arranging the shafts of the respective functional unit at a relatively small, parallel distance, as a result of which an overall compact construction is achieved. Furthermore, the arrangement according to the invention enables the use of the free end regions for the arrangement of additional units in the shafts of the reciprocating piston engine, as described in more detail in claim 8. Finally, with the double use of the reduction gear, a first weight reduction is achieved.

Mit der erfindungsgemäßen Anordnung wird ein besonders einfacher Aufbau einer Mehrzylinder-Hubkolbenmaschine mit integriertem Getriebe nach Anspruch 2 für eine Brennkraftmaschine mit einander gegenüberliegenden Zylindern bzw. Zylinderreihen erreicht. Die mit der erfindungsgemäßen Wellen-Anordnung kombinierte Lage der Teilungsebene in Längserstreckung der Hubkolbenmaschine ermöglicht es in weiterer vorteilhafter Ausgestaltung nach Anspruch 3, einen Boxermotor oder einen V-Motor und ein integriertes Getriebe mit zwei, in der Teilungsebene verbindbaren Gehäusehälften auszubilden. Damit ist ein kompakter Aufbau erreicht, wobei ein wesentlicher Teil der Mechanik der Hubkolbenmaschine sowie des Getriebes in lediglich zwei Gehäusehälften untergebracht ist. Die somit die Mechanik von zwei verschiedenen Funktionsgruppen umschließenden Gehäusehälften sind durch ihre einstückige Ausbildung ferner vorteilhaft für einen steifen Aufbau. Diese einstückigen Gehäuse­hälften ergeben weiter in Druchgußausführung bei steifem Aufbau eine weitere Gewichtsreduzierung.With the arrangement according to the invention, a particularly simple construction of a multi-cylinder reciprocating piston engine with an integrated transmission is achieved for an internal combustion engine with opposing cylinders or cylinder rows. The position of the parting plane in the longitudinal extension of the reciprocating piston machine combined with the shaft arrangement according to the invention makes it possible in a further advantageous embodiment according to claim 3 to form a boxer engine or a V-engine and an integrated gearbox with two housing halves which can be connected in the parting plane. A compact structure is thus achieved, with a substantial part of the mechanics of the reciprocating piston machine and of the transmission being accommodated in only two housing halves. The housing halves thus enclosing the mechanics of two different functional groups are also advantageous for a rigid construction due to their one-piece construction. These one-piece housing halves also result in a further weight reduction in a cast-through design with a rigid construction.

Die erfindungsgemäße Anordnung ermöglicht es ferner, nach einem Teilmerkmal des Anspruches 4, an der Verbindungsstelle der Funktionsgruppe Hubkolbenmaschine mit der Funktionsgruppe Getriebe das Untersetzungsgetriebe mit der Kupplung am Eingang der Getriebe-Eingangswelle zu einer eigenen Funktionsgruppe zusammenzufassen. Entsprechend diesen drei Funktionsgruppen können nach weiteren Merkmalen des Anspruches 4 zwischen der ersten und zweiten sowie zwischen der zweiten und dritten Funktions­gruppe jeweils eine Querwand in dem zweiteiligen Gehäuse für den Boxermotor vorgesehen werden, wodurch im Verbindungsbereich von Maschinengehäuse und Getriebegehäuse eine besonders steife Ausbildung sich ergibt. Diese Ausgestaltung ermöglicht es ferner, das für die Hubkolbenmaschine und das Getriebeaggregat gemeinsame Gehäuse an beiden Enden durch lösbare Deckel abzuschließen, womit die an den freien Endbereichen von Nockenwelle und Kurbel­welle angeordneten weiteren Aggregate zugänglich sind.The arrangement according to the invention also makes it possible, according to a partial feature of claim 4, at the junction of the functional group reciprocating piston engine with the functional group Gearbox to combine the reduction gearbox with the coupling at the input of the gearbox input shaft into a separate function group. According to these three functional groups, a transverse wall can be provided in the two-part housing for the boxer engine between the first and second and between the second and third functional groups, which results in a particularly rigid design in the connection area between the machine housing and the transmission housing. This configuration also makes it possible to close off the housing common to the reciprocating piston machine and the gear unit at both ends by detachable covers, whereby the further units arranged on the free end regions of the camshaft and crankshaft are accessible.

In Verbindung mit den Ansprüchen 3 und 4 ist zur Erzielung eines kompakten Aufbaus nach Anspruch 6 das Untersetzungsgetriebe aus einem mit einem Ritzel der Kurbelwelle kämmenden Rad gebildet, das nach einem weiteren Merkmal des Anspruches 5 einen Korb einer Naßkupplung trägt. Mit der Verwendung einer Naßkupplung sind gegeneinander abzudichtende Räume in vorteilhafter Weise vermieden, so daß auch ein für alle drei Funktionsgruppen "Hubkol­benmaschine", "Untersetzungsgetriebe und Kupplung" sowie "Getrie­beaggregat" ein gemeinsamer Ölsumpf ausgebildet werden kann. Nach einem weiteren Teilmerkmal des Anspruches 5 ist das Rad des Untersetzungsgetriebes mit einem Drehschwingungsdämpfer sowie mit einer Flankenspielausgleichseinrichtung ausgerüstet. Damit erübrigt sich ein gesonderter Dämpfer an der Getriebeeingangswelle, wodurch diese im Aufbau einfacher gestaltet werden kann. Schließ­lich wirkt die Kurbelwelle nach Anspruch 7 am ritzelseitigen Ende mit einer Anlaßeinrichtung zusammen, die mit einem Freilauf ausge­rüstet ist.In conjunction with claims 3 and 4, the reduction gear is formed from a gear meshing with a pinion of the crankshaft to achieve a compact structure according to claim 6, which carries a basket of a wet clutch according to a further feature of claim 5. With the use of a wet clutch, spaces to be sealed against one another are advantageously avoided, so that a common oil sump can also be formed for all three functional groups "reciprocating piston engine", "reduction gear and clutch" and "gear unit". According to a further partial feature of claim 5, the wheel of the reduction gear is equipped with a torsional vibration damper and with a backlash compensation device. This eliminates the need for a separate damper on the transmission input shaft, which makes it easier to design. Finally, the crankshaft cooperates according to claim 7 at the pinion end with a starting device which is equipped with a freewheel.

Die Ausgestaltung der Erfindung im Umfang der Ansprüche 3 mit 8 durch einstückig in Druckgußausführung ausgebildete Gehäusehälften ermöglicht es in vorteilhafter Weise, in eine der Gehäusehälften nicht nur die Kurbelwelle mit ihren an beiden Enden angeordneten Aggregaten zu montieren, sondern auch die aus Nockenwelle, Untersetzungsgetriebe-Rad mit drehfest angeflanschter Kupplung und Getriebe Eingangswelle gebildete Baueinheit in einem Vorgang zu montieren.The embodiment of the invention within the scope of claims 3 to 8 by housing halves formed in one piece in die-cast design advantageously allows not only the crankshaft with its two ends arranged in one of the housing halves Assemblies, but also to assemble the assembly formed from the camshaft, reduction gear wheel with non-rotatably flanged coupling and transmission input shaft in one operation.

Im Rahmen des Anspruches 2 ist ein am Maschinengehäuse anflansch­bares Getriebeaggregat denkbar. Hierfür könnte die Kupplung so ausgestaltet sein, daß am Rad des Untersetzungsgetriebes der Kupplungskorb angeordnet ist und bei der Montage in diesen das auf der Getriebe-Eingangswelle angeordnete Kupplungslamellenpaket eingeschoben wird. Diese Ausgestaltung ist für eine Trockenkupp­lung denkbar.Within the scope of claim 2, a gear unit that can be flanged onto the machine housing is conceivable. For this purpose, the clutch could be designed in such a way that the clutch basket is arranged on the wheel of the reduction gear and the clutch plate pack arranged on the gearbox input shaft is inserted into it during assembly. This configuration is conceivable for a dry clutch.

Im Rahmen der Erfindung kann anstelle der bevorzugten Nockenwellen auch eine weitere Maschinenwelle Verwendung finden mit Ritzeln, die beispielsweise zum Antrieb von im Zylinderkopfbereich der Hubkolbenmaschine angeordnete Nockenwellen antreiben.Within the scope of the invention, instead of the preferred camshafts, a further machine shaft can also be used with pinions which drive, for example, to drive camshafts arranged in the cylinder head region of the reciprocating engine.

Ein bevorzugtes Ausführungsbeispiel der Erfindung ist nachstehend beschrieben. Es zeigt in schematischer Darstellung:

  • Fig. 1 eine Anordnung von Wellen und Aggregaten bei einem in Längsschnitt dargestellten Boxermotor mit gesonderten Gaswechsel-Steuervorrichtung,
  • Fig. 2 den Boxermotor in Stirnansicht.
A preferred embodiment of the invention is described below. It shows in a schematic representation:
  • 1 shows an arrangement of shafts and units in a boxer engine shown in longitudinal section with a separate gas exchange control device,
  • Fig. 2 shows the boxer engine in front view.

Eine Mehrzylinder-Hubkolbenmaschine 1 in der Bauart eines Boxer­motors umfaßt eine Kurbelwelle 2. An einem Ende der Kurbelwelle 2 ist ein Untersetzungsgetriebe 3 angeordnet, das aus einem auf der Kurbelwelle 2 angeordneten Ritzel 4 und einem Rad 5 gebildet ist. Die Untersetzung ist hierbei so gewählt, daß das Rad 5 mit halber Drehzahl der Kurbelwelle 2 dreht. Auf der der Kurbelwelle 2 zugewandten Seite ist das Rad 5 mit einer Nockenwelle 6 drehfest verbunden. Auf der der Kurbelwelle abgewandten Seite steht das Rad 5 mit einer Eingangswelle 7 eines Getriebeaggregates 8 in drehfester Verbindung. Dem Untersetzungsgetriebe 3 ist somit eine Doppelfunktion zugewiesen, indem es zum einen zum Antrieb der Nockenwelle 6 und zum anderen zum Antrieb der Getriebe-Eingangs­welle 7 dient. Aus der vorbeschriebenen Anordnung der Wellen 2 und 6 sowie des Aggregates 8 geht hervor, daß die Kurbelwelle 2 und die Nockenwelle zueinander parallele Drehachsen 2ʹ und 6ʹ (Fig. 2) haben, während die Drehachse 7ʹ der Getriebe-Eingangs­welle 7 mit der Drehachse 6ʹ der Nockenwelle fluchtet.A multi-cylinder reciprocating piston machine 1 in the form of a boxer engine comprises a crankshaft 2. A reduction gear 3 is arranged at one end of the crankshaft 2 and is formed from a pinion 4 arranged on the crankshaft 2 and a wheel 5. The reduction is selected so that the wheel 5 rotates at half the speed of the crankshaft 2. On the side facing the crankshaft 2, the wheel 5 is rotatably connected to a camshaft 6. On the side facing away from the crankshaft, the wheel 5 has an input shaft 7 of a gear unit 8 in non-rotatable connection. The reduction gear 3 is thus assigned a double function in that it serves on the one hand to drive the camshaft 6 and on the other hand to drive the transmission input shaft 7. From the arrangement of the shafts 2 and 6 and the assembly 8 described above, it can be seen that the crankshaft 2 and the camshaft have mutually parallel axes of rotation 2ʹ and 6ʹ (FIG. 2), while the axis of rotation 7ʹ of the transmission input shaft 7 with the axis of rotation 6ʹ Camshaft is aligned.

Wie aus Fig. 2 weiter hervorgeht, sind die Kurbelwelle 2 und die Nockenwelle 6 mit ihren zueinander parallelen Drehachsen 2ʹ und 6ʹ in einer Teilungsebene 9 eines geteilten Maschinengehäuses 10 des Boxermotors 1 mit beidseitig der Teilungsebene 9 vorgesehenen Zylindern 11 und 12 angeordnet. Weiter umfaßt das Getriebeaggregat 8 ein in der Teilungsebene 9 des Maschinengehäuses 10 geteiltes Gehäuse 13. Die auf einer Seite der Teilungsebene 9 benachbarten Teile bzw. Hälften von Getriebe-Gehäuse 13 und Maschinengehäuse 10 sind miteinander einstückig in Druckguß als Druckgußteile 14 und 15 ausgebildet. Zur Erzielung steifer und kompakter Druckguß­teile 14 und 15 sind im Verbindungsbereich von Maschinengehäuse 10 und Getriebegehäuse 13 mit Lagerstellen für die jeweiligen Wellen, wie Kurbelwelle 2, Nockenwelle 6, Getriebe-Eingangswelle 7, ausgerüstete Querwände 16 und 17 derart beabstandet angeordnet, daß zwischen der maschinengehäuseseitigen Querwand 16 und der getriebegehäuseseitigen Querwand 17 sowohl das Untersetzungsgetrie­be 3 als auch eine dessen Rad 5 mit der Eingangswelle 7 des Getriebe-aggregates 8 drehfest verbindende Kupplung 18 angeordnet ist. Da die in der Trennebene miteinander verschraubten, jeweils einstückigen Druckgußteile 14 und 15 zum einen einen erheblichen Teil der Mechanik des Boxermotors 1 und zum anderen die Mechanik des Getriebeaggregates 8 umschließen, wird zur Vermeidung kompli­zierter Abdichtungen für diese beiden Funktionsgruppen als Kupplung 18 eine Naßkupplung gewählt. Wie aus Fig. 1 weiter ersichtlich, bilden das Untersetzungsgetriebe 3 und die Naßkupplung 18 eine dritte Funktionsgruppe zwischen der ersten Funktionsgruppe des Boxermotors 1 und der zweiten Funktionsgruppe des Getriebeaggrega­ tes 8. Alle drei Funktionsgruppen stehen mit einem gemeinsamen Ölsumpf 19 in Verbindung, dessen Spiegel 20 durch eine strichlier­te Linie angedeutet ist.As can further be seen from FIG. 2, the crankshaft 2 and the camshaft 6 with their mutually parallel axes of rotation 2ʹ and 6ʹ are arranged in a parting plane 9 of a divided machine housing 10 of the boxer engine 1 with cylinders 11 and 12 provided on both sides of the parting plane 9. The gear unit 8 further comprises a housing 13 divided in the parting plane 9 of the machine housing 10. The parts or halves of the gearbox housing 13 and the machine housing 10 which are adjacent on one side of the parting plane 9 are integrally formed with one another in die casting as die cast parts 14 and 15. To achieve stiff and compact die-cast parts 14 and 15, in the connection area of the machine housing 10 and gear housing 13 with bearing points for the respective shafts, such as crankshaft 2, camshaft 6, transmission input shaft 7, equipped transverse walls 16 and 17 are arranged so spaced that between the machine housing side The transverse wall 16 and the transverse wall 17 on the gearbox housing side both the reduction gear 3 and one of its wheels 5 with the input shaft 7 of the gear unit 8 are arranged in a rotationally fixed coupling 18. Since the one-piece die-cast parts 14 and 15, which are screwed together in the parting plane, on the one hand enclose a considerable part of the mechanics of the boxer engine 1 and on the other hand the mechanics of the gear unit 8, a wet clutch is selected as the clutch 18 to avoid complicated seals for these two functional groups. As can also be seen from FIG. 1, the reduction gear 3 and the wet clutch 18 form a third functional group between the first functional group of the boxer engine 1 and the second functional group of the gear unit tes 8. All three functional groups are connected to a common oil sump 19, the mirror 20 of which is indicated by a dashed line.

Die Naßkupplung 18 wirkt über einen Korb 21 mit dem Rad 5 drehfest zusammen. Das Rad 5 ist ferner mit einem Drehschwingungs­dämpfer 22 ausgerüstet. Damit kann ein gesonderter Schwingungs­dämpfer für die Getriebe-Eingangswelle 7 entfallen. Für einen kompakten Aufbau des Boxermotors 1 kämmt das Rad 5 des Unter­setzungsgetriebes 3 direkt mit dem auf der Kurbelwelle 2 angeord­neten Ritzel 4. Zur Geräuschreduzierung kann das Rad 5 ferner mit einer Flankenspielausgleichseinrichtung (nicht dargestellt) ausgerüstet sein.The wet clutch 18 cooperates with the wheel 5 in a rotationally fixed manner via a basket 21. The wheel 5 is also equipped with a torsional vibration damper 22. A separate vibration damper for the transmission input shaft 7 can thus be dispensed with. For a compact construction of the boxer engine 1, the wheel 5 of the reduction gear 3 meshes directly with the pinion 4 arranged on the crankshaft 2. To reduce noise, the wheel 5 can also be equipped with a backlash compensation device (not shown).

Der Boxermotor 1 ist stirnseitig durch einen Deckel 23 und das Getriebeaggregat 8 abtriebsseitig durch einen Deckel 24 verschlos­sen. Der abnehmbare Deckel 23 ermöglicht den Zugang zu einem im Endbereich der Kurbelwelle 2 angeordneten Generator 25 sowie zu einem Zündgeber 26 und einer Ölpumpe 27, die auf der Nockenwelle 6 angeordnet sind. Schließlich wirkt die Kurbelwelle 2 am ritzel­seitigen Ende mit einer Anlaßeinrichtung 28 zusammen, die einen Anlasser 29 umfaßt, dessen Ritzel 30 mit einem Zahnrad 31 kämmt. Das Zahnrad 31 der Anlaßeinrichtung 28 ist mit dem Ritzel 4 des Untersetzungsgetriebes 3 gleichachsig angeordnet und steht mit diesem über einen Freilauf 32 in Verbindung. Der Freilauf 32 dient nach dem Starten des Boxermotors 1 als Überhol-Freilauf.The boxer engine 1 is closed on the front side by a cover 23 and the gear unit 8 on the output side by a cover 24. The removable cover 23 enables access to a generator 25 arranged in the end region of the crankshaft 2 and to an ignition transmitter 26 and an oil pump 27 which are arranged on the camshaft 6. Finally, the crankshaft 2 cooperates at the pinion end with a starter device 28 which includes a starter 29, the pinion 30 of which meshes with a toothed wheel 31. The gear wheel 31 of the starter device 28 is arranged coaxially with the pinion 4 of the reduction gear 3 and is connected to it via a freewheel 32. After starting the boxer engine 1, the freewheel 32 serves as an overrunning freewheel.

Claims (8)

1. Anordnung von Wellen und Aggregaten bei Mehrzylinder-Hubkol­benmaschinen mit gesonderten Gaswechsel-Steuervorrichtungen, insbesondere Brennkraftmaschinen,
- umfassend eine Gaswechselventile steuernde Nockenwelle (6),
- die von einer Kurbelwelle (2) angetrieben ist, und
- wobei die Kurbelwelle weiter über ein Untersetzungsgetriebe (3) mit einer Eingangswelle (7) eines Getriebeaggregates (8) in Antriebsverbindung steht, und
- der Eingangswelle eine Kupplung (18) zugeordnet ist, dadurch gekennzeichnet,
- daß das Untersetzungsgetriebe (3) an einem Ende der Kurbel­welle (2) angeordnet ist und
- ein mit halber Drehzahl der Kurbelwelle drehendes Rad (5) umfaßt, das
- auf der der Kurbelwelle zugewandten Seite mit einer weiteren Maschinenwelle (Nockenwelle 6) und
- auf der der Kurbelwelle abgewandten Seite mit der Eingangs­welle (7) des Getriebeaggregates (8) in drehfester Verbindung steht.1. Arrangement of shafts and units in multi-cylinder reciprocating piston machines with separate gas exchange control devices, in particular internal combustion engines,
- comprising a camshaft (6) controlling gas exchange valves,
- Which is driven by a crankshaft (2), and
- The crankshaft is further connected via a reduction gear (3) to an input shaft (7) of a gear unit (8), and
- A coupling (18) is assigned to the input shaft, characterized in that
- That the reduction gear (3) is arranged at one end of the crankshaft (2) and
- A wheel rotating at half speed of the crankshaft (5), the
- On the side facing the crankshaft with another machine shaft (camshaft 6) and
- Is on the side facing away from the crankshaft with the input shaft (7) of the gear unit (8) in a rotationally fixed connection. 2. Anordnung nach Anspruch 1, dadurch gekennzeichnet,
- daß Kurbelwelle (2) und Nockenwelle (6) mit ihren Drehachsen in einer Teilungsebene (9) eines längsgeteilten Maschinenge­häuses (10) einer Hubkolbenmaschine (Boxermotor 1) mit beidseitig der Teilungsebene vorgesehenen Zylindern (11,12) angeordnet sind,
- daß das Getriebeaggregat (8) ein in der Teilungsebene (9) des Maschinengehäuses (10) geteiltes Gehäuse (13) umfaßt,
- wobei jedes Teil bzw. jede Hälfte des Getriebe-Gehäuses (13) mit dem benachbarten Teil bzw. der benachbarten Hälfte des Maschinengehäuses (10) verbunden ist.2. Arrangement according to claim 1, characterized in
- That the crankshaft (2) and camshaft (6) are arranged with their axes of rotation in a parting plane (9) of a longitudinally divided machine housing (10) of a reciprocating piston engine (boxer engine 1) with cylinders (11, 12) provided on both sides of the parting plane,
- That the gear unit (8) comprises a divided in the division plane (9) of the machine housing (10) housing (13),
- Wherein each part or half of the gear housing (13) is connected to the adjacent part or half of the machine housing (10). 3. Anordnung nach Anspruch 2, dadurch gekennzeichnet, daß die auf einer Seite der Teilungsebene (9) benachbarten Teile bzw. Hälften von Getriebe-Gehäuse (13) und Maschinengehäuse (10) miteinander einstückig in Guß (Druckgußteile 14,15) ausgebildet sind.3. Arrangement according to claim 2, characterized in that on one side of the parting plane (9) adjacent parts or halves of the gear housing (13) and machine housing (10) are integrally formed in one piece in cast (die-cast parts 14, 15). 4. Anordnung nach Anspruch 2 oder 3, dadurch gekennzeichnet,
- daß im Verbindungsbereich von Maschinengehäuse (10) und Getriebe-Gehäuse (13) mit Lagerstellen für die jeweiligen Wellen (Kurbelwelle 2, Nockenwelle 6; Eingangswelle 7, Vorge­legewelle) ausgerüstete Querwände (16,17) derart beabstandet angeordnet sind,
- daß zwischen der maschinengehäuseseitigen Querwand (16) und der getriebegehäuseseitigen Querwand (17) sowohl das Untersetzungsgetriebe (3) als auch
- eine dessen Rad (5) mit der Eingangswelle (7) des Getriebe­aggregates (8) drehfest verbindende Kupplung (Naßkupplung 18) angeordnet ist.4. Arrangement according to claim 2 or 3, characterized in
- That in the connection area of the machine housing (10) and gear housing (13) with bearing points for the respective shafts (crankshaft 2, camshaft 6; input shaft 7, countershaft) equipped transverse walls (16, 17) are arranged so spaced apart,
- That between the machine housing side transverse wall (16) and the gear housing side transverse wall (17) both the reduction gear (3) and
- One of whose wheels (5) with the input shaft (7) of the gear unit (8) rotatably connecting coupling (wet clutch 18) is arranged. 5. Anordnung nach den Ansprüchen 3 und 4, dadurch gekennzeichnet,
- daß am Rad (5) des Untersetzungsgetriebes (3) ein Korb (21) einer Naßkupplung (18) drehfest angeordnet ist, und
- daß das Rad (5) ferner mit einem Drehschwingungsdämpfer (22) sowie mit einer Flankenspielaufgleichs-Einrichtung aus­gerüstet ist.5. Arrangement according to claims 3 and 4, characterized in
- That on the wheel (5) of the reduction gear (3), a basket (21) of a wet clutch (18) is rotatably arranged, and
- That the wheel (5) is also equipped with a torsional vibration damper (22) and with a backlash compensation device. 6. Anordnung nach den Ansprüchen 4 und 5, dadurch gekennzeichnet, daß das Untersetzungsgetriebe (3) ein mit dem Rad (5) kämmendes, auf der Kurbelwelle (2) angeordnetes Ritzel (4) umfaßt.6. Arrangement according to claims 4 and 5, characterized in that the reduction gear (3) comprises a meshing with the wheel (5) on the crankshaft (2) arranged pinion (4). 7. Anordnung nach den Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Kurbelwelle (2) am ritzelseitigen Ende mit einer Anlaßeinrichtung (28) zusammenwirkt, die mit einem Freilauf (32) zwischen einem Zahnrad (31) und dem Ritzel (4) ausge­rüstet ist.7. Arrangement according to claims 1 to 6, characterized in that the crankshaft (2) cooperates at the pinion end with a starter device (28) equipped with a freewheel (32) between a gear (31) and the pinion (4) is. 8. Anordnung nach den Ansprüchen 1 bis 7, dadurch gekennzeich­net, daß in den übrigen Endbereichen von Nockenwelle (6) und Kurbelwelle (2) weitere Aggregate (Zündgeber 26, Ölpumpe 27; Generator 25) angeordnet sind.8. Arrangement according to claims 1 to 7, characterized in that in the other end regions of the camshaft (6) and crankshaft (2) further units (ignition transmitter 26, oil pump 27; generator 25) are arranged.
EP86116066A 1985-11-22 1986-11-20 Multicylinder reciprocating-piston machine, in particular internal-combustion engine Expired - Lifetime EP0223248B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853541315 DE3541315A1 (en) 1985-11-22 1985-11-22 ARRANGEMENT OF SHAFTS AND UNITS IN MULTI-CYLINDER PISTON PISTON MACHINES WITH SEPARATE GAS EXCHANGE CONTROL DEVICES, IN PARTICULAR COMBUSTION ENGINES
DE3541315 1985-11-22

Publications (3)

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EP0223248A2 true EP0223248A2 (en) 1987-05-27
EP0223248A3 EP0223248A3 (en) 1987-09-16
EP0223248B1 EP0223248B1 (en) 1990-10-03

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Application Number Title Priority Date Filing Date
EP86116066A Expired - Lifetime EP0223248B1 (en) 1985-11-22 1986-11-20 Multicylinder reciprocating-piston machine, in particular internal-combustion engine

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DE102018207830A1 (en) * 2018-05-18 2019-11-21 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with two cylinders

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DE102018207830A1 (en) * 2018-05-18 2019-11-21 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with two cylinders

Also Published As

Publication number Publication date
DE3541315A1 (en) 1987-05-27
EP0223248A3 (en) 1987-09-16
EP0223248B1 (en) 1990-10-03
DE3674725D1 (en) 1990-11-08

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