WO2013110470A1 - Multi-joint crank drive of an internal combustion engine, and method for assembling a multi-joint crank drive - Google Patents
Multi-joint crank drive of an internal combustion engine, and method for assembling a multi-joint crank drive Download PDFInfo
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- WO2013110470A1 WO2013110470A1 PCT/EP2013/000240 EP2013000240W WO2013110470A1 WO 2013110470 A1 WO2013110470 A1 WO 2013110470A1 EP 2013000240 W EP2013000240 W EP 2013000240W WO 2013110470 A1 WO2013110470 A1 WO 2013110470A1
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- eccentric shaft
- combustion engine
- internal combustion
- support tube
- crank drive
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/18—Eccentric-shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
- F16C3/023—Shafts; Axles made of several parts, e.g. by welding
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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
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/22—Internal combustion engines
Definitions
- the invention relates to a multi-link crank drive of an internal combustion engine, with a plurality of rotatably mounted on crank pins of a crankshaft coupling links and a plurality of rotatably mounted on crank pin eccentric shaft Anschpleueln, each of the coupling links is pivotally connected to a piston connecting rod of a piston of the internal combustion engine and one of the Anlenkpleueln.
- the invention further relates to a method for assembling a multi-joint crank drive.
- the multi-link crank drive of the type mentioned is known from the prior art. It is usually part of the internal combustion engine, but can also be used in other areas.
- the multi-joint crank drive comprises the eccentric shaft whose rotation angle can be adjusted by means of an adjusting device, in particular as a function of an operating point of the internal combustion engine. Alternatively, the eccentric shaft can also be operatively connected to a crankshaft of the internal combustion engine and in this way be drivable by this.
- the multi-link crank drive has a number of coupling pistons corresponding to the number of pistons of the internal combustion engine, each of which is rotatably mounted on the corresponding crank pin of the crankshaft and has two arms protruding beyond the crankshaft on opposite sides and each having a pivot joint at its end.
- One of the pivot joints is used for pivotal connection with the piston connecting rod, which connects one of the pistons of the internal combustion engine via the coupling member with the crankshaft.
- Another of the pivot joints is used for pivotal connection with the so-called Anlenkpleuel, which is rotatably mounted with its other end on the crank pin of the eccentric shaft.
- the compression ratio achieved in the cylinder assigned to the respective piston can be set, in particular as a function of the operating point of the internal combustion engine and / or the power stroke.
- the eccentric shaft is brought into a specific, the desired compression ratio corresponding angular position or the phase angle between the eccentric shaft and the crankshaft to a certain value.
- the well-known multi-joint crank drive has a forged and
- the eccentric shaft is present as a built shaft and a support tube, at least one eccentric to an axis of rotation of the eccentric eccentric, formed separately from the support tube crank pin and at least one separately formed from the support tube transmission element.
- the eccentric shaft is therefore not present as a one-piece element, but is assembled during assembly of the multi-joint crank mechanism of individual parts, wherein the individual parts in particular the support tube, the at least one crank pin and the transmission element comprise.
- the support tube is preferably a circular cylinder which is circular over its entire length. Separated from this, the crank pin and the transmission element are formed or manufactured.
- the eccentric shaft has a stop and / or encoder wheel. This is provided as an additional element and can for example form at least one end stop, so that the eccentric shaft can be arranged only under a rotational angle contained in a certain rotation angle range. Likewise, it may be formed as a sender wheel, by means of which the present angle of rotation of the eccentric shaft and / or their speed can be determined.
- a development of the invention provides that the Anlenkpleueln each have a Anlenkpleuelauge whose inner wall is directly in sliding contact with the crank pin.
- the Anlenkpleuelauge surrounds the crank pin in the circumferential direction - relative to a rotation axis of the eccentric shaft - preferably completely.
- the Anlenkpleuelauge usually has a bearing bush and is about this only indirectly with the crank pin in sliding contact.
- the built eccentric shaft allows the inner wall of the Anlenkpleuelauges can be placed directly on the crank pin, without a lower durability is expected.
- the crank pin can be provided with a coating, in particular DLC coating (diamond-like carbon coating). Such a coating can be applied to a forged eccentric shaft only at great expense and correspondingly high costs.
- the inner wall of the Anlenkpleuelauges is solidified by rolling or other suitable method.
- a development of the invention provides that the support tube is closed at least on one side with a closure part.
- a closure part for example, serve a sealing plug.
- the closure member prevents dirt and / or moisture from penetrating into the interior of the support tube and may possibly have a corrosive effect there. It is therefore particularly advantageous if the support tube has on both sides in each case such a closure part and is closed by means of this. If the closure part is designed as a sealing plug, it is pushed into the carrier tube during the assembly of the multi-joint cure drive and is then held in a force-fit manner there.
- the invention further relates to a method for assembling a multi-joint crank drive, in particular according to the preceding embodiments, wherein the multi-joint crank drive a plurality of rotatably mounted on crank pin crankshaft coupling members and a plurality of rotatably mounted on crank pin eccentric shaft Anschpleueln, each of the coupling members pivotally is connected to a piston connecting rod of a piston of the internal combustion engine and one of the Anlenkpleuel.
- the eccentric shaft in the assembly of the multi-joint crank drive from a support tube, at least one eccentric to a rotational axis of the eccentric shaft, formed separately from the support tube crank pin and at least one formed separately from the support tube gear element is built.
- the multi-joint crank drive or the eccentric shaft can be developed according to the above statements. The advantages realized in this way have already been discussed above.
- crank pin and the gear element are applied to the support tube and then attached by friction welding, internal high pressure forming or shrinking at this.
- additional elements such as the crank pin and the gear element, but for example, the stop and / or encoder wheel
- they are attached to the support tube.
- a welding method such as friction welding serve.
- the support tube can be widened by forming, so that the elements are subsequently held securely to him.
- hydroforming is used.
- the elements can be secured by shrinking on the support tube.
- the support tube is usually cooled and the, for example, held by a device arranged for this, elements attached to the support tube. In a subsequent heating of the support tube to ambient temperature, this widens, so that the elements are held securely.
- the additional elements and not the support tube may be deformed.
- crank pins are subjected to a coating process during their manufacture or assembly of the multi-link crank drive with their outer surface in contact contact or sliding contact after assembly with the inner wall of the Anlenkpleuelauges.
- a coating such as a DLC coating
- a plurality of crank pins are made from a Hubzapfenrohling. Before the Hubzapfenrohling is divided by a separation process in several Hubzapfen, the above-mentioned coating can be applied to him. In that regard, not every single crank pin must be provided separately with the coating.
- Figure 1 is a perspective view of a portion of an internal combustion engine, and 2 shows a longitudinal section through an eccentric shaft.
- the internal combustion engine 1 shows a perspective view of a portion of an internal combustion engine 1, which as a series internal combustion engine, more specifically as a four-stroke four-cylinder in-line engine is present.
- the internal combustion engine 1 has a crankshaft 2 and four pistons 3, each of which is movably mounted in one of four cylinders, not shown, of the internal combustion engine 1.
- Each of the four pistons 3 is connected to the crankshaft 2 by a piston connecting rod 4.
- crankshaft 2 is rotatably mounted in shaft bearings (not shown) of a cylinder crankcase of the internal combustion engine 1 also not shown and has five serving for storage centric shaft journal 5 and four crank pin 6 (of which in the figure only one is visible), whose longitudinal center axes in different Angle alignments are offset parallel to a rotation axis 7 of the crankshaft 2.
- the internal combustion engine 1 further comprises an eccentric shaft 8, which preferably has an axis of rotation 7 parallel to the axis of rotation 7 of the crankshaft 2.
- the eccentric shaft 8 is rotatably mounted, for example, next to the crankshaft 2 and slightly below this in the cylinder crankcase and coupled to the crankshaft 2.
- the multi-joint crank eb 10 comprises a total of four coupling members 11, which are each rotatably mounted on one of the crank pin 6 of the crankshaft 2.
- Each of the coupling members 11 has a lifting arm 12, which is connected via a pivot joint 13 pivotally connected to a lower end of one of Kolbenpleuel 4.
- An upper end of the respective Kolbenpleuels 4 is articulated via a further pivot joint 14 on the associated piston 3.
- each of the four pistons 3 is connected to the crankshaft 2 by the respective piston connecting rod 4 and the respective coupling member 11.
- the ehrgelenkskurbeltrieb 10 further comprises a number of Kolbenpleuel 4 and the coupling members 11 corresponding number of Anlenkpleueln 15. These are, for example, approximately parallel to the Kolbenpleueln 4 aligned and in the axial direction of the crankshaft 2 and the eccentric shaft 8 in each case approximately the same plane as the associated Kolbenpleuel 4, but arranged on the opposite side of the crankshaft 2.
- Each Anlenkpleuel 15 comprises a connecting rod 16 and two at opposite ends of the connecting rod 16 arranged connecting rod eyes 17, 18, in particular with different inner diameters.
- the larger connecting rod 18 of each Anlenkpleuels 15 at the lower end of the connecting rod 16 surrounds a relative to the axis of rotation 9 of the eccentric shaft 8 eccentric crank pin 19 of the eccentric shaft 8, on the Anschpleuel 15 is rotatably supported by means of a rotary bearing 20.
- the smaller connecting rod eye 17 at the upper end of the connecting rod 16 of each Anlenkpleuels 15 forms part of a pivot joint 21 between the Anlenkpleuel 15 and a longer coupling arm 22 of the adjacent coupling member 11, which protrudes on the opposite to the lifting arm 12 side of the crankshaft 2 on this.
- the eccentric shaft 8 has between adjacent eccentric crank pin 19 and at their ends for supporting the eccentric shaft 8 in shaft bearings serving, to the axis of rotation 10 coaxial shaft sections 23. Apart from a variable compression can be reduced by the arrangement described above, the inclination of the Kolbenpleueln 4 with respect to the cylinder axis of the associated cylinder during rotation of the crankshaft 2, resulting in a reduction of the piston side forces and thus the frictional forces between the piston 2 and cylinder walls of the Cylinder leads.
- a working stroke of the pistons 3 can be selected or set as a function of a momentary power stroke of the internal combustion engine.
- the eccentric shaft 8 is driven by a not shown here eccentric shaft gear from the crankshaft 2.
- the eccentric shaft gear comprises at least one gear element 2 (not shown) arranged on the eccentric shaft 8.
- FIG. 2 shows a longitudinal section through the eccentric shaft 8. It becomes clear that the latter is in the form of a built-up shaft and comprises at least one support tube 25, which is of hollow cylindrical construction, the crank pin 19 and the gear element 24, which is for example in the form of a toothed wheel. In addition, a stop and / or encoder wheel 26 may be arranged on the carrier tube 25.
- the shaft sections 23, which serve as bearings, are merely indicated here.
- FIG. 2 shows that a cavity 27 present in the carrier tube 25 is closed by means of closure parts 28 present on both sides of the carrier tube 25.
- the closure parts 28 are designed in particular as sealing plugs, that is to say they are introduced into the carrier tube 25 when the multi-joint cure drive 10 or the internal combustion engine 1 is mounted in such a way that they are subsequently held in a non-positive manner in the latter.
- the elements shown here, such as the crank pins 19, the gear element 24 and the stop and / or encoder wheel 26 are applied to the carrier tube 25 and then attached thereto, for example by friction welding, hydroforming or shrinking. In principle, however, the attachment can be realized in any manner.
- the presented here eccentric shaft 8 means a respect to conventional eccentric waves significantly reduced Hersrties- and thus cost.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The invention relates to a multi-joint crank drive (10) of an internal combustion engine (1), comprising a plurality of coupling elements (11) which are rotatably mounted on crankpins (6) of a crankshaft (2) and comprising a plurality of articulated connecting rods (15) which are rotatably mounted on crankpins (19) of an eccentric shaft (8). Each coupling element (11) is pivotally connected to a piston connecting rod (4) of a piston (3) of the internal combustion engine (1) and to one of the articulated connecting rods (15). The eccentric shaft (8) is present as an assembled shaft and has a support pipe (25), at least one crankpin (19) which is eccentric relative to a rotational axis (9) of the eccentric shaft (8) and which is designed separately from the support pipe (25), and at least one transmission element (24) which is designed separately from the support pipe (25). The invention further relates to a method for assembling a multi-joint crank drive (10).
Description
Mehrgelenkskurbeltrieb einer Brennkraftmaschine sowie Verfahren Multi-joint crank drive of an internal combustion engine and method
zur Montage eines Mehrgelenkskurbeltriebs for mounting a multi-link crank drive
Die Erfindung betrifft einen Mehrgelenkskurbeltrieb einer Brennkraftmaschine, mit einer Mehrzahl von drehbar auf Hubzapfen einer Kurbelwelle gelagerten Koppelgliedern und einer Mehrzahl von drehbar auf Hubzapfen einer Exzenterwelle gelagerten Anlenkpleueln, wobei jedes der Koppelglieder schwenkbar mit einem Kolbenpleuel eines Kolbens der Brennkraftmaschine und einem der Anlenkpleueln verbunden ist. Die Erfindung betrifft weiterhin ein Verfahren zur Montage eines Mehrgelenkskurbeltriebs. The invention relates to a multi-link crank drive of an internal combustion engine, with a plurality of rotatably mounted on crank pins of a crankshaft coupling links and a plurality of rotatably mounted on crank pin eccentric shaft Anlenkpleueln, each of the coupling links is pivotally connected to a piston connecting rod of a piston of the internal combustion engine and one of the Anlenkpleueln. The invention further relates to a method for assembling a multi-joint crank drive.
Der Mehrgelenkskurbeltrieb der eingangs genannten Art ist aus dem Stand der Technik bekannt. Er ist üblicherweise Bestandteil der Brennkraftmaschine, kann jedoch auch in anderen Bereichen Anwendung finden. Der Mehrgelenkskurbeltrieb umfasst die Exzenterwelle, deren Drehwinkel mittels einer Stelleinrichtung, insbesondere in Abhängigkeit von einem Betriebspunkt der Brennkraftmaschine, verstellt werden kann. Alternativ kann die Exzenterwelle auch mit einer Kurbelwelle der Brennkraftmaschine wirkverbunden und auf diese Weise von dieser antreibbar sein. Der Mehrgelenkskurbeltrieb verfügt über eine der Anzahl der Kolben der Brennkraftmaschine entsprechende Anzahl von Koppelgliedern, die jeweils drehbar auf dem entsprechenden Hubzapfen der Kurbelwelle gelagert sind und zwei nach entgegengesetzten Seiten über die Kurbelwelle überstehende, an ihrem Ende jeweils mit einem Schwenkgelenk versehene Arme aufweisen. Eines der Schwenkgelenke dient zur schwenkbaren Verbindung mit dem Kolbenpleuel, der einen der Kolben der Brennkraftmaschine über das Koppelglied mit der Kurbelwelle verbindet. Ein anderes der Schwenkgelenke dient zur schwenkbaren Verbindung mit dem sogenannten Anlenkpleuel, welcher mit seinem anderen Ende drehbar auf dem Hubzapfen der Exzenterwelle gelagert ist. The multi-link crank drive of the type mentioned is known from the prior art. It is usually part of the internal combustion engine, but can also be used in other areas. The multi-joint crank drive comprises the eccentric shaft whose rotation angle can be adjusted by means of an adjusting device, in particular as a function of an operating point of the internal combustion engine. Alternatively, the eccentric shaft can also be operatively connected to a crankshaft of the internal combustion engine and in this way be drivable by this. The multi-link crank drive has a number of coupling pistons corresponding to the number of pistons of the internal combustion engine, each of which is rotatably mounted on the corresponding crank pin of the crankshaft and has two arms protruding beyond the crankshaft on opposite sides and each having a pivot joint at its end. One of the pivot joints is used for pivotal connection with the piston connecting rod, which connects one of the pistons of the internal combustion engine via the coupling member with the crankshaft. Another of the pivot joints is used for pivotal connection with the so-called Anlenkpleuel, which is rotatably mounted with its other end on the crank pin of the eccentric shaft.
Mittels des Mehrgelenkskurbeltriebs kann das in dem dem Kolben jeweils zugeordneten Zylinder erreichte Verdichtungsverhältnis eingestellt werden, insbesondere in Abhängigkeit von dem Betriebspunkt der Brennkraftmaschine und/oder dem Arbeitstakt. Zum Verstellen des Verdichtungsverhältnisses wird die Exzenterwelle in eine bestimmte, dem gewünschten Verdichtungsverhältnis entsprechende Drehwinkelstellung gebracht oder die Phasenlage zwischen der Exzenterwelle und der Kurbelwelle auf einen bestimmten Wert eingestellt. Der bekannte Mehrgelenkskurbeltrieb weist eine geschmiedete und By means of the multi-joint crank drive, the compression ratio achieved in the cylinder assigned to the respective piston can be set, in particular as a function of the operating point of the internal combustion engine and / or the power stroke. To adjust the compression ratio, the eccentric shaft is brought into a specific, the desired compression ratio corresponding angular position or the phase angle between the eccentric shaft and the crankshaft to a certain value. The well-known multi-joint crank drive has a forged and
BESTÄTSGUÜNÜGSKOPIE
anschließend bearbeitete Exzenterwelle auf. Die Herstellung einer solchen Exzenterwelle ist jedoch sehr aufwendig. BESTÄTSGUÜNÜGSKOPIE subsequently machined eccentric shaft. However, the production of such eccentric shaft is very expensive.
Aus dem Stand der Technik ist beispielsweise die Druckschrift EP 1 178 194 A2 bekannt. Diese beschreibt eine Brennkraftmaschine mit einem variablen Verdichtungsverhältnis. Zum Einstellen des Verdichtungsverhältnisses ist eine Exzenterwelle vorgesehen, welche über Anlenkpleuel mit drehbar gelagerten Koppelgliedern wirkverbunden ist. Auf der der Exzenterwelle zugewandten Seite jedes Anlenkpleuels ist dabei ein geteiltes Pleuelauge vorgesehen, um eine einfache Montage des jeweiligen Anlenkpleuels an der Exzenterwelle zu ermöglichen. The document EP 1 178 194 A2, for example, discloses the state of the art. This describes an internal combustion engine with a variable compression ratio. To set the compression ratio, an eccentric shaft is provided, which is operatively connected via Anlenkpleuel with rotatably mounted coupling members. On the eccentric shaft side facing each Anlenkpleuels a split connecting rod is provided to allow easy mounting of the respective Anlenkpleuels on the eccentric shaft.
Es ist daher Aufgabe der Erfindung, einen Mehrgelenkskurbeltrieb einer Brennkraftmaschine vorzuschlagen, welches den eingangs genannten Nachteil nicht aufweist, sondern insbesondere eine einfach und kostengünstig herzustellende Exzenterwelle aufweist. It is therefore an object of the invention to provide a multi-joint crank drive of an internal combustion engine, which does not have the disadvantage mentioned above, but in particular has a simple and inexpensive to produce eccentric shaft.
Dies wird erfindungsgemäß mit einem Mehrgelenkskurbeltrieb mit den Merkmalen des Anspruchs 1 erreicht. Dabei ist vorgesehen, dass die Exzenterwelle als gebaute Welle vorliegt und ein Trägerrohr, wenigstens einen zu einer Drehachse der Exzenterwelle exzentrischen, getrennt von dem Trägerrohr ausgebildeten Hubzapfen sowie zumindest ein getrennt von dem Trägerrohr ausgebildetes Getriebeelement aufweist. Die Exzenterwelle liegt also nicht als einstückiges Element vor, sondern wird bei der Montage des Mehrgelenkskurbeltriebs aus Einzelteilen zusammengesetzt, wobei die Einzelteile insbesondere das Trägerrohr, den wenigstens einen Hubzapfen und das Getriebeelement umfassen. Das Trägerrohr ist vorzugsweise ein über seine gesamte Länge kreisrunder Hohlzylinder. Getrennt von diesem werden der Hubzapfen und das Getriebeelement ausgebildet beziehungsweise hergestellt. Bei der Montage des Mehrgelenkskurbeltriebs werden also das Trägerrohr, der Hubzapfen und das Getriebeelement als voneinander separate Elemente bereitgestellt. Erst bei der Montage werden die Elemente miteinander verbunden und aneinander befestigt. Entsprechend wird der Herstellungsaufwand für die Exzenterwelle deutlich reduziert. This is achieved according to the invention with a multi-joint crank mechanism with the features of claim 1. It is provided that the eccentric shaft is present as a built shaft and a support tube, at least one eccentric to an axis of rotation of the eccentric eccentric, formed separately from the support tube crank pin and at least one separately formed from the support tube transmission element. The eccentric shaft is therefore not present as a one-piece element, but is assembled during assembly of the multi-joint crank mechanism of individual parts, wherein the individual parts in particular the support tube, the at least one crank pin and the transmission element comprise. The support tube is preferably a circular cylinder which is circular over its entire length. Separated from this, the crank pin and the transmission element are formed or manufactured. When mounting the multi-joint crank drive so the support tube, the crank pin and the transmission element are provided as separate elements. Only during assembly, the elements are connected and fastened together. Accordingly, the production cost for the eccentric shaft is significantly reduced.
Eine Weiterbildung der Erfindung sieht vor, dass die Exzenterwelle ein Anschlagsund/oder Geberrad aufweist. Dieses ist als zusätzliches Element vorgesehen und kann beispielsweise wenigstens einen Endanschlag ausbilden, sodass die Exzenterwelle lediglich unter einem in einem bestimmten Drehwinkelbereich enthaltenen Drehwinkel angeordnet werden kann. Ebenso kann es als Geberrad ausgebildet sein, mittels welchem
der momentan vorliegende Drehwinkel der Exzenterwelle und/oder ihre Drehzahl bestimmt werden können. A development of the invention provides that the eccentric shaft has a stop and / or encoder wheel. This is provided as an additional element and can for example form at least one end stop, so that the eccentric shaft can be arranged only under a rotational angle contained in a certain rotation angle range. Likewise, it may be formed as a sender wheel, by means of which the present angle of rotation of the eccentric shaft and / or their speed can be determined.
Eine Weiterbildung der Erfindung sieht vor, dass die Anlenkpleueln jeweils ein Anlenkpleuelauge aufweisen, dessen Innenwand unmittelbar mit dem Hubzapfen in Gleitkontakt steht. Das Anlenkpleuelauge umschließt den Hubzapfen in Umfangsrichtung - bezogen auf eine Drehachse der Exzenterwelle - vorzugsweise vollständig. Bei bekannten Mehrgelenkskurbeltrieben weist das Anlenkpleuelauge üblicherweise eine Lagerbuchse auf und steht über diese lediglich mittelbar mit dem Hubzapfen in Gleitkontakt. Die gebaute Exzenterwelle erlaubt es jedoch, dass die Innenwand des Anlenkpleuelauges unmittelbar auf den Hubzapfen aufgesetzt werden kann, ohne dass eine geringere Betriebsfestigkeit zu erwarten ist. Beispielsweise kann dazu der Hubzapfen mit einer Beschichtung, insbesondere DLC-Beschichtung (Diamond-like Carbon- Beschichtung), versehen sein. Eine solche Beschichtung ist nur unter hohem Aufwand und entsprechend hohen Kosten auf eine geschmiedete Exzenterwelle aufbringbar. Zusätzlich kann es vorgesehen sein, dass die Innenwand des Anlenkpleuelauges durch Rollieren oder andere geeignete Verfahren verfestigt wird. A development of the invention provides that the Anlenkpleueln each have a Anlenkpleuelauge whose inner wall is directly in sliding contact with the crank pin. The Anlenkpleuelauge surrounds the crank pin in the circumferential direction - relative to a rotation axis of the eccentric shaft - preferably completely. In known multi-link crank drives, the Anlenkpleuelauge usually has a bearing bush and is about this only indirectly with the crank pin in sliding contact. The built eccentric shaft, however, allows the inner wall of the Anlenkpleuelauges can be placed directly on the crank pin, without a lower durability is expected. For example, for this purpose the crank pin can be provided with a coating, in particular DLC coating (diamond-like carbon coating). Such a coating can be applied to a forged eccentric shaft only at great expense and correspondingly high costs. In addition, it may be provided that the inner wall of the Anlenkpleuelauges is solidified by rolling or other suitable method.
Eine Weiterbildung der Erfindung sieht vor, dass das Trägerrohr zumindest einseitig mit einem Verschlussteil verschlossen ist. Als Verschlussteil kann beispielsweise ein Verschlussstopfen dienen. Das Verschlussteil verhindert, dass Schmutz und/oder Feuchtigkeit in das Innere des Trägerrohrs eindringen und dort unter Umständen korrosiv wirken können. Besonders vorteilhaft ist es daher, wenn das Trägerrohr beidseitig jeweils ein solches Verschlussteil aufweist und mittels diesem verschlossen ist. Ist das Verschlussteil als Verschlussstopfen ausgebildet, so wird es bei der Montage des Mehrgelenkskur- beltriebs in das Trägerrohr eingeschoben und ist dort anschließend kraftschlüssig gehalten. A development of the invention provides that the support tube is closed at least on one side with a closure part. As a closure part, for example, serve a sealing plug. The closure member prevents dirt and / or moisture from penetrating into the interior of the support tube and may possibly have a corrosive effect there. It is therefore particularly advantageous if the support tube has on both sides in each case such a closure part and is closed by means of this. If the closure part is designed as a sealing plug, it is pushed into the carrier tube during the assembly of the multi-joint cure drive and is then held in a force-fit manner there.
Die Erfindung betrifft weiterhin ein Verfahren zur Montage eines Mehrgelenkkurbeltriebs, insbesondere gemäß den vorstehenden Ausführungen, wobei der Mehrgelenkskurbel- trieb eine Mehrzahl von drehbar auf Hubzapfen einer Kurbelwelle gelagerten Koppelgliedern und eine Mehrzahl von drehbar auf Hubzapfen einer Exzenterwelle gelagerten Anlenkpleueln aufweist, wobei jedes der Koppelglieder schwenkbar mit einem Kolbenpleuel eines Kolbens der Brennkraftmaschine und einem der Anlenkpleuel verbunden wird. Dabei ist vorgesehen, dass die Exzenterwelle bei der Montage des Mehrgelenks- kurbeltriebs aus einem Trägerrohr, wenigstens einem zu einer Drehachse der Exzenterwelle exzentrischen, getrennt von dem Trägerrohr ausgebildeten Hubzapfen sowie zu-
mindest einem getrennt von dem Trägerrohr ausgebildeten Getriebeelement gebaut wird. Der Mehrgelenkskurbeltrieb beziehungsweise die Exzenterwelle kann gemäß den vorstehenden Ausführungen weitergebildet sein. Auf die auf diese Weise realisierten Vorteile wurde bereits vorstehend eingegangen. The invention further relates to a method for assembling a multi-joint crank drive, in particular according to the preceding embodiments, wherein the multi-joint crank drive a plurality of rotatably mounted on crank pin crankshaft coupling members and a plurality of rotatably mounted on crank pin eccentric shaft Anlenkpleueln, each of the coupling members pivotally is connected to a piston connecting rod of a piston of the internal combustion engine and one of the Anlenkpleuel. It is provided that the eccentric shaft in the assembly of the multi-joint crank drive from a support tube, at least one eccentric to a rotational axis of the eccentric shaft, formed separately from the support tube crank pin and at least one formed separately from the support tube gear element is built. The multi-joint crank drive or the eccentric shaft can be developed according to the above statements. The advantages realized in this way have already been discussed above.
Eine Weiterbildung der Erfindung sieht vor, dass der Hubzapfen und das Getriebeelement auf das Trägerrohr aufgebracht und anschließend durch Reibschweißen, Innen- hochdruckumformen oder Schrumpfen an dieser befestigt werden. Nach dem Aufbringen der zusätzlichen Elemente, wie dem Hubzapfen und dem Getriebeelement, jedoch beispielsweise auch dem Anschlag- und/oder Geberrad, werden diese an dem Trägerrohr befestigt. Zu diesem Zweck kann insbesondere ein Schweißverfahren, wie Reibschweißen, dienen. Alternativ kann jedoch auch das Trägerrohr durch Umformen aufgeweitet werden, sodass die Elemente nachfolgend sicher an ihm gehalten sind. Dabei kommt beispielsweise Innenhochdruckumformen zum Einsatz. Ebenso können die Elemente durch Schrumpfen auf dem Trägerrohr befestigt werden. Dabei wird üblicherweise das Trägerrohr gekühlt und die, beispielsweise von einer dazu eingerichteten Vorrichtung gehaltenen, Elemente auf das Trägerrohr aufgesteckt. Bei einem nachfolgenden Erwärmen des Trägerrohrs auf Umgebungstemperatur weitet sich dieses auf, sodass die Elemente sicher gehalten sind. Alternativ können bei dem Schrumpfen auch die zusätzlichen Elemente und nicht das Trägerrohr verformt werden. A development of the invention provides that the crank pin and the gear element are applied to the support tube and then attached by friction welding, internal high pressure forming or shrinking at this. After applying the additional elements, such as the crank pin and the gear element, but for example, the stop and / or encoder wheel, they are attached to the support tube. For this purpose, in particular a welding method, such as friction welding serve. Alternatively, however, the support tube can be widened by forming, so that the elements are subsequently held securely to him. Here, for example, hydroforming is used. Likewise, the elements can be secured by shrinking on the support tube. In this case, the support tube is usually cooled and the, for example, held by a device arranged for this, elements attached to the support tube. In a subsequent heating of the support tube to ambient temperature, this widens, so that the elements are held securely. Alternatively, during shrinkage, the additional elements and not the support tube may be deformed.
Besonders vorteilhaft ist es selbstverständlich, wenn die Hubzapfen bei ihrer Herstellung beziehungsweise der Montage des Mehrgelenkskurbeltriebs mit ihrer nach der Montage mit der Innenwand des Anlenkpleuelauges in Berührkontakt beziehungsweise Gleitkontakt stehenden Außenfläche einem Beschichtungsverfahren unterzogen werden. Bei diesem kann eine Beschichtung, beispielsweise eine DLC-Beschichtung, aufgebracht werden. Bevorzugt werden mehrere Hubzapfen aus einem Hubzapfenrohling hergestellt. Bevor der Hubzapfenrohling durch ein Trennverfahren in mehrere Hubzapfen aufgeteilt wird, kann die vorstehend genannte Beschichtung auf ihn aufgebracht werden. Insoweit muss nicht jeder einzelne Hubzapfen getrennt mit der Beschichtung versehen werden. It is of course of particular advantage when the crank pins are subjected to a coating process during their manufacture or assembly of the multi-link crank drive with their outer surface in contact contact or sliding contact after assembly with the inner wall of the Anlenkpleuelauges. In this, a coating, such as a DLC coating, are applied. Preferably, a plurality of crank pins are made from a Hubzapfenrohling. Before the Hubzapfenrohling is divided by a separation process in several Hubzapfen, the above-mentioned coating can be applied to him. In that regard, not every single crank pin must be provided separately with the coating.
Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert, ohne dass eine Beschränkung der Erfindung erfolgt. Dabei zeigen: The invention will be explained in more detail with reference to the embodiments illustrated in the drawings, without any limitation of the invention. Showing:
Figur 1 eine perspektivische Ansicht eines Bereichs einer Brennkraftmaschine, und
Figur 2 einen Längsschnitt durch eine Exzenterwelle. Figure 1 is a perspective view of a portion of an internal combustion engine, and 2 shows a longitudinal section through an eccentric shaft.
Die Figur 1 zeigt eine perspektivische Ansicht eines Bereichs einer Brennkraftmaschine 1 , welche als Reihenbrennkraftmaschine, genauer gesagt als Viertakt-Vierzylinder- Reihenbrennkraftmaschine, vorliegt. Die Brennkraftmaschine 1 verfügt über eine Kurbelwelle 2 und vier Kolben 3, von welchen jeder in einem von vier nicht dargestellten Zylindern der Brennkraftmaschine 1 beweglich gelagert ist. Jeder der vier Kolben 3 ist durch ein Kolbenpleuel 4 mit der Kurbelwelle 2 verbunden. Die Kurbelwelle 2 ist in hier nicht dargestellten Wellenlagern eines ebenfalls nicht dargestellten Zylinderkurbelgehäuses der Brennkraftmaschine 1 drehbar gelagert und weist fünf zur Lagerung dienende zentrische Wellenzapfen 5 sowie vier Hubzapfen 6 (von welchen in der Figur jeweils nur einer sichtbar ist) auf, deren Längsmittelachsen in unterschiedlichen Winkelausrichtungen parallel zu einer Drehachse 7 der Kurbelwelle 2 versetzt sind. 1 shows a perspective view of a portion of an internal combustion engine 1, which as a series internal combustion engine, more specifically as a four-stroke four-cylinder in-line engine is present. The internal combustion engine 1 has a crankshaft 2 and four pistons 3, each of which is movably mounted in one of four cylinders, not shown, of the internal combustion engine 1. Each of the four pistons 3 is connected to the crankshaft 2 by a piston connecting rod 4. The crankshaft 2 is rotatably mounted in shaft bearings (not shown) of a cylinder crankcase of the internal combustion engine 1 also not shown and has five serving for storage centric shaft journal 5 and four crank pin 6 (of which in the figure only one is visible), whose longitudinal center axes in different Angle alignments are offset parallel to a rotation axis 7 of the crankshaft 2.
Die Brennkraftmaschine 1 umfasst weiter eine Exzenterwelle 8, die bevorzugt eine zur Drehachse 7 der Kurbelwelle 2 parallele Drehachse 9 aufweist. Die Exzenterwelle 8 ist beispielsweise neben der Kurbelwelle 2 sowie etwas unterhalb von dieser im Zylinderkurbelgehäuse drehbar gelagert und mit der Kurbelwelle 2 gekoppelt. Neben der Kurbelwelle 2 und der Exzenterwelle 8 umfasst der Mehrgelenkskurbelt eb 10 insgesamt vier Koppelglieder 11 , die jeweils auf einem der Hubzapfen 6 der Kurbelwelle 2 drehbar gelagert sind. Jedes der Koppelglieder 11 weist einen Hubarm 12 auf, der über ein Schwenkgelenk 13 schwenkbar mit einem unteren Ende von einem der Kolbenpleuel 4 verbunden ist. Ein oberes Ende des jeweiligen Kolbenpleuels 4 ist über ein weiteres Schwenkgelenk 14 am zugehörigen Kolben 3 angelenkt. Insgesamt ist also jeder der vier Kolben 3 durch den jeweiligen Kolbenpleuel 4 und das jeweilige Koppelglied 11 mit der Kurbelwelle 2 verbunden. The internal combustion engine 1 further comprises an eccentric shaft 8, which preferably has an axis of rotation 7 parallel to the axis of rotation 7 of the crankshaft 2. The eccentric shaft 8 is rotatably mounted, for example, next to the crankshaft 2 and slightly below this in the cylinder crankcase and coupled to the crankshaft 2. In addition to the crankshaft 2 and the eccentric shaft 8, the multi-joint crank eb 10 comprises a total of four coupling members 11, which are each rotatably mounted on one of the crank pin 6 of the crankshaft 2. Each of the coupling members 11 has a lifting arm 12, which is connected via a pivot joint 13 pivotally connected to a lower end of one of Kolbenpleuel 4. An upper end of the respective Kolbenpleuels 4 is articulated via a further pivot joint 14 on the associated piston 3. Overall, therefore, each of the four pistons 3 is connected to the crankshaft 2 by the respective piston connecting rod 4 and the respective coupling member 11.
Der ehrgelenkskurbeltrieb 10 umfasst weiter eine der Anzahl der Kolbenpleuel 4 und der Koppelglieder 11 entsprechende Anzahl von Anlenkpleueln 15. Diese sind beispielsweise ungefähr parallel zu den Kolbenpleueln 4 ausgerichtet und in axialer Richtung der Kurbelwelle 2 und der Exzenterwelle 8 jeweils in etwa derselben Ebene wie der dazugehörige Kolbenpleuel 4, jedoch auf der entgegengesetzten Seite der Kurbelwelle 2, angeordnet. Jeder Anlenkpleuel 15 umfasst eine Pleuelstange 16 und zwei an entgegengesetzten Enden der Pleuelstange 16 angeordnete Pleuelaugen 17, 18, insbesondere mit unterschiedlichen inneren Durchmessern. Das größere Pleuelauge 18 jedes Anlenkpleuels 15 am unteren Ende der Pleuelstange 16 umgibt einen in Bezug zur Drehachse 9 der Exzenterwelle 8 exzentrischen Hubzapfen 19 der Exzenterwelle 8, auf
dem der Anlenkpleuel 15 mittels eines Drehlagers 20 drehbar gelagert ist. Das kleinere Pleuelauge 17 am oberen Ende der Pleuelstange 16 jedes Anlenkpleuels 15 bildet einen Teil eines Schwenkgelenks 21 zwischen dem Anlenkpleuel 15 und einem längeren Koppelarm 22 des benachbarten Koppelglieds 11 , der auf der zum Hubarm 12 entgegengesetzten Seite der Kurbelwelle 2 über diese übersteht. The ehrgelenkskurbeltrieb 10 further comprises a number of Kolbenpleuel 4 and the coupling members 11 corresponding number of Anlenkpleueln 15. These are, for example, approximately parallel to the Kolbenpleueln 4 aligned and in the axial direction of the crankshaft 2 and the eccentric shaft 8 in each case approximately the same plane as the associated Kolbenpleuel 4, but arranged on the opposite side of the crankshaft 2. Each Anlenkpleuel 15 comprises a connecting rod 16 and two at opposite ends of the connecting rod 16 arranged connecting rod eyes 17, 18, in particular with different inner diameters. The larger connecting rod 18 of each Anlenkpleuels 15 at the lower end of the connecting rod 16 surrounds a relative to the axis of rotation 9 of the eccentric shaft 8 eccentric crank pin 19 of the eccentric shaft 8, on the Anlenkpleuel 15 is rotatably supported by means of a rotary bearing 20. The smaller connecting rod eye 17 at the upper end of the connecting rod 16 of each Anlenkpleuels 15 forms part of a pivot joint 21 between the Anlenkpleuel 15 and a longer coupling arm 22 of the adjacent coupling member 11, which protrudes on the opposite to the lifting arm 12 side of the crankshaft 2 on this.
Die Exzenterwelle 8 weist zwischen benachbarten exzentrischen Hubzapfen 19 sowie an ihren Stirnenden zur Lagerung der Exzenterwelle 8 in Wellenlagern dienende, zur Drehachse 10 koaxiale Wellenabschnitte 23 auf. Abgesehen von einer variablen Verdichtung kann durch die zuvor beschriebene Anordnung auch die Neigung der Kolbenpleueln 4 in Bezug zur Zylinderachse der zugehörigen Zylinder während der Drehung der Kurbelwelle 2 verringert werden, was zu einer Verringerung der Kolbenseitenkräfte und damit der Reibkräfte zwischen den Kolben 2 und Zylinderwänden der Zylinder führt. Insgesamt kann mit dem hier beschriebenen Mehrgelenkskurbeltrieb ein Arbeitshub der Kolben 3 in Abhängigkeit von einem momentanen Arbeitstakt der Brennkraftmaschine gewählt beziehungsweise eingestellt werden. Zu diesem Zweck ist die Exzenterwelle 8 über ein hier nicht dargestelltes Exzenterwellengetriebe von der Kurbelwelle 2 angetrieben. Das Ex- zenterwellengetriebe umfasst zumindest ein auf der Exzenterwelle 8 angeordnetes Getriebeelement 2 (nicht dargestellt). The eccentric shaft 8 has between adjacent eccentric crank pin 19 and at their ends for supporting the eccentric shaft 8 in shaft bearings serving, to the axis of rotation 10 coaxial shaft sections 23. Apart from a variable compression can be reduced by the arrangement described above, the inclination of the Kolbenpleueln 4 with respect to the cylinder axis of the associated cylinder during rotation of the crankshaft 2, resulting in a reduction of the piston side forces and thus the frictional forces between the piston 2 and cylinder walls of the Cylinder leads. Overall, with the multi-link crank drive described here, a working stroke of the pistons 3 can be selected or set as a function of a momentary power stroke of the internal combustion engine. For this purpose, the eccentric shaft 8 is driven by a not shown here eccentric shaft gear from the crankshaft 2. The eccentric shaft gear comprises at least one gear element 2 (not shown) arranged on the eccentric shaft 8.
Die Figur 2 zeigt einen Längsschnitt durch die Exzenterwelle 8. Dabei wird deutlich, dass diese als gebaute Welle vorliegt und zumindest aus einem Trägerrohr 25, welches hohlzylindrisch aufgebaut ist, den Hubzapfen 19 und dem Getriebeelement 24, welches beispielsweise als Zahnrad vorliegt, besteht. Zusätzlich kann auf dem Trägerrohr 25 ein Anschlags- und/oder Geberrad 26 angeordnet sein. Die Wellenabschnitte 23, welche als Lagerstellen dienen, sind hier lediglich angedeutet. Die Figur 2 zeigt, dass ein in dem Trägerrohr 25 vorliegender Hohlraum 27 mittels beidseitig an dem Trägerrohr 25 vorliegenden Verschlussteilen 28 verschlossen ist. Die Verschlussteile 28 sind insbesondere als Verschlussstopfen ausgebildet, werden also bei der Montage des Mehrgelenkskur- beltriebs 10 beziehungsweise der Brennkraftmaschine 1 in das Trägerrohr 25 derart eingebracht, dass sie nachfolgend kraftschlüssig in diesem gehalten sind. Zur Herstellung der Exzenterwelle 8 werden die hier dargestellten Elemente, wie die Hubzapfen 19, das Getriebeelement 24 und das Anschlags- und/oder Geberrad 26 auf das Trägerrohr 25 aufgebracht und anschließend an diesem befestigt, beispielsweise durch Reibschweißen, Innenhochdruckumformen oder Schrumpfen. Prinzipiell ist jedoch die Befestigung auf beliebige Art und Weise realisierbar. Die hier vorgestellte Exzenterwelle 8 bedeutet
einen gegenüber üblichen Exzenterwellen deutlich verringerten Hersteilungs- und damit Kostenaufwand.
FIG. 2 shows a longitudinal section through the eccentric shaft 8. It becomes clear that the latter is in the form of a built-up shaft and comprises at least one support tube 25, which is of hollow cylindrical construction, the crank pin 19 and the gear element 24, which is for example in the form of a toothed wheel. In addition, a stop and / or encoder wheel 26 may be arranged on the carrier tube 25. The shaft sections 23, which serve as bearings, are merely indicated here. FIG. 2 shows that a cavity 27 present in the carrier tube 25 is closed by means of closure parts 28 present on both sides of the carrier tube 25. The closure parts 28 are designed in particular as sealing plugs, that is to say they are introduced into the carrier tube 25 when the multi-joint cure drive 10 or the internal combustion engine 1 is mounted in such a way that they are subsequently held in a non-positive manner in the latter. To produce the eccentric shaft 8, the elements shown here, such as the crank pins 19, the gear element 24 and the stop and / or encoder wheel 26 are applied to the carrier tube 25 and then attached thereto, for example by friction welding, hydroforming or shrinking. In principle, however, the attachment can be realized in any manner. The presented here eccentric shaft 8 means a respect to conventional eccentric waves significantly reduced Hersteilungs- and thus cost.
BEZUGSZEICHENLISTE LIST OF REFERENCE NUMBERS
Brennkraftmaschine Internal combustion engine
Kurbelwelle crankshaft
Kolben piston
Kolbenpleuel Kolbenpleuel
Wellenzapfen shaft journal
Hubzapfen crank pins
Drehachse axis of rotation
Exzenterwelle eccentric shaft
Drehachse axis of rotation
Mehrgelenkskurbeltrieb Multi-joint crank drive
Koppelglied coupling member
Hubarm lifting arm
Schwenkgelenk pivot
Schwenkgelenk pivot
Anlenkpleuel articulation connecting rod
Pleuelstange connecting rod
Pleuelauge connecting rod
Pleuelauge connecting rod
Hubzapfen crank pins
Drehlager pivot bearing
Schwenkgelenk pivot
Koppelarm coupling arm
Wellenabschnitt shaft section
Getriebeelement gear element
Trägerrohr support tube
Anschlags- und/oder Geberrad Stop and / or encoder wheel
Hohlraum cavity
Verschlussteil
closing part
Claims
1. ehrgelenkskurbeltrieb (10) einer Brennkraftmaschine (1), mit einer Mehrzahl von drehbar auf Hubzapfen (6) einer Kurbelwelle (2) gelagerten Koppelgliedern (11) und einer Mehrzahl von drehbar auf Hubzapfen (19) einer Exzenterwelle (8) gelagerten Anlenkpleueln (15), wobei jedes der Koppelglieder (11) schwenkbar mit einem Kolbenpleuel (4) eines Kolbens (3) der Brennkraftmaschine (1) und einem der Anlenkpleuel (15) verbunden ist, dadurch gekennzeichnet, dass die Exzenterwelle (8) als gebaute Welle vorliegt und ein Trägerrohr (25), wenigstens einen zu einer Drehachse (9) der Exzenterwelle (8) exzentrischen, getrennt von dem Trägerrohr (25) ausgebildeten Hubzapfen (19) sowie zumindest ein getrennt von dem Trägerrohr (25) ausgebildetes Getriebeelement (24) aufweist. 1. ehrgelenkskurbeltrieb (10) an internal combustion engine (1), with a plurality of rotatably mounted on crank pin (6) of a crankshaft (2) mounted coupling members (11) and a plurality of rotatably mounted on crank pins (19) of an eccentric shaft (8) Anlenkpleueln ( 15), wherein each of the coupling members (11) is pivotally connected to a Kolbenpleuel (4) of a piston (3) of the internal combustion engine (1) and one of the Anlenkpleuel (15), characterized in that the eccentric shaft (8) is present as a built shaft and a support tube (25), at least one to a rotation axis (9) of the eccentric shaft (8) formed separately from the support tube (25) Hubzapfen (19) and at least one separate from the support tube (25) formed gear element (24) ,
2. Mehrgelenkskurbeltrieb nach Anspruch 1, dadurch gekennzeichnet, dass die Exzenterwelle (8) ein Anschlags- und/oder Geberrad (26) aufweist. 2. multi-link crank drive according to claim 1, characterized in that the eccentric shaft (8) has a stop and / or encoder wheel (26).
3. Mehrgelenkskurbeltrieb nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Anlenkpleuel (15) jeweils ein Anlenkpleuelauge (18) aufweisen, dessen Innenwand unmittelbar mit dem Hubzapfen (19) in Gleitkontakt steht. 3. Multi-link crank drive according to one of the preceding claims, characterized in that the Anlenkpleuel (15) each have a Anlenkpleuelauge (18) whose inner wall is directly in sliding contact with the crank pin (19).
4. Mehrgelenkskurbeltrieb nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Trägerrohr (25) zumindest einseitig mit einem Verschlussteil (28) verschlossen ist. 4. Multi-link crank drive according to one of the preceding claims, characterized in that the carrier tube (25) is closed at least on one side with a closure part (28).
5. Verfahren zur Montage eines Mehrgelenkkurbeltriebs (10) einer Brennkraftmaschine (1), insbesondere gemäß einem oder mehreren der vorhergehenden Ansprüche, wobei der Mehrgelenkskurbeltrieb (10) eine Mehrzahl von drehbar auf Hubzapfen (6) einer Kurbelwelle (2) gelagerten Koppelgliedern (11) und eine Mehrzahl von drehbar auf Hubzapfen (19) einer Exzenterwelle (8) gelagerten Anlenkpleueln (15) aufweist, wobei jedes der Koppelglieder (11) schwenkbar mit einem Kolbenpleuel (4) eines Kolbens (3) der Brennkraftmaschine (1) und einem der Anlenkpleuel (15) verbunden wird, dadurch gekennzeichnet, dass die Exzenterwelle (8) bei der Montage des Mehrgelenkskurbeltriebs (10) aus einem Trägerrohr (25), wenigstens einem zu einer Drehachse (9) der Exzenterwelle (8) exzentrischen, getrennt von dem Trägerrohr (25) ausgebildeten Hubzapfen (19) sowie zumindest einem getrennt von dem Trägerrohr (25) ausgebildeten Getriebeelement (24) gebaut wird. 5. A method for assembling a multi-joint crank drive (10) of an internal combustion engine (1), in particular according to one or more of the preceding claims, wherein the multi-joint crank drive (10) has a plurality of coupling elements (11) rotatably mounted on crank pins (6) of a crankshaft (2). and a plurality of pivotable on crank pin (19) of an eccentric shaft (8) mounted Anlenkpleueln (15), wherein each of the coupling members (11) pivotally connected to a Kolbenpleuel (4) of a Piston (3) of the internal combustion engine (1) and one of the Anlenkpleuel (15) is connected, characterized in that the eccentric shaft (8) during assembly of the multi-joint crank drive (10) from a support tube (25), at least one to an axis of rotation (9 ) of the eccentric shaft (8) eccentric, separate from the support tube (25) formed Hubzapfen (19) and at least one separate from the support tube (25) formed transmission element (24) is built.
6. Verfahren nach Anspruch 5, dadurch gekennzeichnet, dass der Hubzapfen (19) und das Getriebeelement (24) auf das Trägerrohr (25) aufgebracht und anschließend durch Reibschweißen, Innenhochdruckumfor- men oder Schrumpfen an diesem befestigt werden. 6. The method according to claim 5, characterized in that the crank pin (19) and the gear element (24) applied to the support tube (25) and then by friction welding, hydroforming or shrinking attached thereto.
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DE102012001648.4A DE102012001648B4 (en) | 2012-01-27 | 2012-01-27 | Multi-joint crank drive of an internal combustion engine and method for assembling a multi-link crank drive |
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JP2010180806A (en) * | 2009-02-06 | 2010-08-19 | Nissan Motor Co Ltd | Variable compression ratio device of internal combustion engine |
-
2012
- 2012-01-27 DE DE102012001648.4A patent/DE102012001648B4/en not_active Expired - Fee Related
-
2013
- 2013-01-28 WO PCT/EP2013/000240 patent/WO2013110470A1/en not_active Application Discontinuation
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EP1178194A2 (en) | 2000-07-31 | 2002-02-06 | Nissan Motor Company, Limited | Internal combustion engine with variable compression ratio mechanism |
JP2003322036A (en) * | 2002-05-07 | 2003-11-14 | Nissan Motor Co Ltd | Variable compression ratio mechanism of internal- combustion engine |
EP1505276A1 (en) * | 2003-08-08 | 2005-02-09 | Toyota Jidosha Kabushiki Kaisha | Variable compression ratio mechanism |
JP2007211706A (en) * | 2006-02-10 | 2007-08-23 | Nissan Motor Co Ltd | Variable compression ratio mechanism for internal combustion engine |
JP2010014046A (en) * | 2008-07-04 | 2010-01-21 | Toyota Motor Corp | Engine with variable compression ratio |
JP2010133374A (en) * | 2008-12-08 | 2010-06-17 | Nissan Motor Co Ltd | Control shaft for variable compression ratio engine |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2021016690A1 (en) * | 2019-07-28 | 2021-02-04 | Goncalves Pereira Almir | Device for variation of compression ratio |
US11879400B2 (en) | 2019-07-28 | 2024-01-23 | Almir Gonçalves Pereira | Variable compression ratio device |
Also Published As
Publication number | Publication date |
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DE102012001648B4 (en) | 2014-04-30 |
DE102012001648A1 (en) | 2013-08-01 |
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