WO2017129175A1 - Reciprocating piston internal combustion engine having a variable compression ratio - Google Patents
Reciprocating piston internal combustion engine having a variable compression ratio Download PDFInfo
- Publication number
- WO2017129175A1 WO2017129175A1 PCT/DE2017/100044 DE2017100044W WO2017129175A1 WO 2017129175 A1 WO2017129175 A1 WO 2017129175A1 DE 2017100044 W DE2017100044 W DE 2017100044W WO 2017129175 A1 WO2017129175 A1 WO 2017129175A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- internal combustion
- combustion engine
- reciprocating internal
- eccentric
- engine according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Ceased
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—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
Definitions
- the invention relates to a reciprocating internal combustion engine with variable Verdich- ratio, which comprises an eccentric on which a Maupleuel is articulated, which interacts via an intermediate lever with a crankshaft and a connecting rod, the latter connecting rod is pivotally mounted on a piston of the internal combustion engine.
- Such a reciprocating internal combustion engine is for example from the
- WO 2007/057149 A1 An intermediate lever of this reciprocating internal combustion engine, which has a variable compression ratio, is referred to as a transverse lever.
- the transverse lever is articulated at three points with other components of the reciprocating internal combustion engine. These are connections to a Maupleuel, a crankpin of a crankshaft, and a connecting rod, which is referred to in the case of WO 2007/057149 A1 as a connecting rod.
- the hinged to a piston of the engine connecting rod is thus not coupled directly to the crankshaft, but via the cross lever.
- the remote from the cross lever end of Maupleuels is adjustable by means of an eccentric.
- the various rotational and pivot points and centers of gravity of the individual elements of the known reciprocating internal combustion engine with variable compression ratio should be such that inertial and centrifugal forces that arise when moving the individual elements, superimpose such that they cancel each other at least partially.
- the reciprocating internal combustion engine can be designed in four-cylinder design.
- DE 10 2010 032 427 A1 discloses an adjusting device for a reciprocating piston engine with variable compression, which is designed as a hydraulic adjusting device.
- an electrohydraulic actuator is provided for adjusting the compression ratio of an internal combustion engine.
- variable compression ratio reciprocating internal combustion engines have a constant compression ratio reciprocating internal combustion engine having the advantage that they can be operated at low load with high compression ratio, and thus particularly fuel efficient and in the case of high power demand with reduced compression ratio and simultaneous boost, typically turbocharging.
- the invention has for its object to provide a reciprocating internal combustion engine with variable compression ratio, which is distinguished from the cited prior art by a particularly favorable ratio between long-term robustness, mechanical precision and manufacturing effort.
- a reciprocating internal combustion engine having the features of claim 1.
- This is a reciprocating internal combustion engine with variable compression ratio, which comprises an eccentric in a known basic structure, to which a Maupleuel is hinged, on the other hand via an intermediate lever with the crankshaft of the internal combustion engine and with a mounted on a piston of the internal combustion engine Pleu- el interacts.
- a linear drive is provided for adjusting the eccentric, which is coupled via a Verstellpleuel with an adjustment of the eccentric. The linear drive allows the eccentric to be operated with moderate forces and at the same time with very good mechanical precision.
- the linear drive is a screw drive.
- Screw drives are both low-play interpretable and rational to produce.
- the screw is self-locking.
- the self-locking screw drive can have a simple movement thread.
- the self-locking of the screw drive is synonymous with the fact that once a compression ratio of the Hubkolbenbrennkraftmaschi- ne remains constant without power supply of the linear drive.
- the screw drive is preferably a ball screw or other Wälzgewindetrieb, which has rolling elements, for example, rollers, between the threaded spindle and the spindle nut.
- the lack of self-locking of the screw drive has the advantage that in case of failure of the power supply of the linear drive of the eccentric can automatically assume a preferred position, which is associated with a normal setting of the compression ratio.
- the pitch of a non-self-locking screw drive is typically greater than the pitch of a self-locking screw drive.
- higher drive torques would be required to operate the non-self-locking screw drive compared to the self-locking screw drive, but this is due to the lower friction properties of the non-self-locking screw drive. partially compensated or even overcompensated.
- the non-self-locking screw drive is particularly suitable.
- the self-locking screw drive is characterized by the fact that during operation of the reciprocating internal combustion engine, lower or even no holding elements, which hold the linear drive in a constant position, are required.
- the adjustment of the eccentric is preferably pivotable over an angle of more than 90 °.
- the secondary actuating mechanism comprises the eccentric, the intermediate lever and the connecting rod, which is mounted on the combustion chamber limiting piston of the internal combustion engine.
- the two actuating gears have specific torque transfer functions. Each torque transfer function indicates the ratio between the introduced torque and the output torque of the respective adjusting gear.
- the torque transmitting function of the primary actuating gear has a single maximum and the torque transmitting function of the secondary actuating gear a single minimum, wherein the extreme values of the two torque transmitting functions are approximately in the middle of the adjustment.
- the series connection of the two adjusting gears ensures that a resulting total torque transfer function, which is the ratio between the Force, which is generated at the output of the secondary actuating gear, and the required drive torque of the linear drive indicates that has a lower translation bandwidth than each of the two individual torque-transmitting functions.
- a resulting total torque transfer function which is the ratio between the Force, which is generated at the output of the secondary actuating gear, and the required drive torque of the linear drive indicates that has a lower translation bandwidth than each of the two individual torque-transmitting functions.
- the ratio between generated force at the output of the secondary actuating gear and drive torque, which is introduced into the input side of the primary adjusting gear, over the entire adjustment range is at least approximately constant.
- the linear drive which serves to adjust the eccentric, is preferably driven electrically.
- another, for example hydraulic, drive of the provided for pivoting the adjustment of the eccentric linear drive is possible.
- FIG. 2 shows a detail from the arrangement according to FIG. 1, FIG.
- Figures 1 and 2 and Figures 7, 8, 9 show in various, not to scale lent illustrations features of a generally designated by the reference numeral 1 adjusting mechanism for varying the compression ratio of a reciprocating internal combustion engine, for example in the form of a multi-cylinder in-line engine.
- the reference numeral 1 adjusting mechanism for varying the compression ratio of a reciprocating internal combustion engine, for example in the form of a multi-cylinder in-line engine.
- the adjusting mechanism 1 is composed of two actuators 2, 3 connected in series, namely a primary actuating gear 2 and a secondary actuating gear 3.
- a common element of both control gear 2, 3 is an eccentric 4, wherein a pivoting of the eccentric 4 by an adjustment 5, which is attributable to the primary control gear 2, is possible.
- On the eccentric 4 a Maupleuel 6 is hinged, which is pivotally coupled to an intermediate lever 7.
- the intermediate lever 7 has a triangular basic shape and is coupled to a crankshaft 8 on a crank pin 9.
- a connecting rod 1 1 is articulated.
- the Pleuelanlenkddling 10 is also referred to as a lower connecting rod bearing.
- An upper connecting rod bearing is denoted by 12 and establishes the connection to a piston 13 of the internal combustion engine.
- the terms "lower” and “upper” connecting rod bearings do not imply any statement about the installation position.
- the pivot axis about which the adjustment arm 5 is pivotable is designated SW.
- the corresponding adjustment angle (FIGS. 3, 4, 5) is designated V and the entire adjustment range of the adjustment arm 5 is VB.
- the adjustment 5 is coupled to a Verstellpleuel 14 which is articulated to a first Verstellpleuellagerddling 15 of the adjustment 5.
- a second adjusting splined 16 provides an articulated connection between the Verstellpleuel 14 and a spindle nut 17.
- the spindle nut 17 is part of a linear drive 18, softer further comprises a threaded spindle 19 and is designed as a ball screw.
- the threaded spindle 19 is rotatably supported by means of two rolling bearings 20, 21; the spindle nut 17 is exclusively displaceable.
- an electric motor 22 is provided to drive the threaded spindle 19, an electric motor 22 is provided.
- a first torque transfer function MDI outlined in FIG. 3 represents the relationship between the torque acting in the adjusting arm 5, that is, at the output of the primary adjusting gear 2, and the torque applied by the electric motor 22 and thus acting in the threaded spindle 19 as a function of the adjusting angle V.
- the torque transfer function MDI describes a curve with a curvature that has the same sign over the entire adjustment range VB. In the middle position of the adjustment arm 5 (corresponding to FIG. 8) designated M, the torque transfer function MDI has a maximum.
- FIG. 4 shows the torque transmission function of the secondary adjusting gear 3 designated MD2.
- a single minimum is in the region of the center position M of the adjusting arm 5, while the torque transmitting function MD2 is located at the edges of the adjusting range VB. is ximal.
- a total torque transmission function denoted MDG which is illustrated in an idealized manner in FIG. 5, is the result of the series connection of the primary actuating gear 2 and the secondary actuating gear 3. As clearly shown in FIG. 5, this is to be applied by the electric motor 2 for actuating the adjusting mechanism 1 Torque over the entire adjustment range VB practically constant.
- the design of the linear drive 18 as a non-self-locking screw drive is synonymous with the fact that its efficiency ⁇ is greater than 50%.
- the slope of the threaded spindle 19 and of the spindle nut 17, designated St, is greater than in typical screw geometries used in mechanical engineering. With reference to the diagram of FIG. 6, this means that both the slope St and the efficiency ⁇ of the linear drive 18 are in the upper range.
- a slope St can be selected in the lower region, which is associated with a significantly reduced efficiency ⁇ , as shown in FIG. 6 can be seen, in which case rolling elements in Linear actuator 18 omitted, that is, a simple motion thread exists.
- the primary actuating gear 2 is designed as a self-locking gear.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Transmission Devices (AREA)
Abstract
Description
Hubkolbenbrennkraftmaschine mit veränderlichem Verdichtungsverhältnis Reciprocating internal combustion engine with variable compression ratio
Die Erfindung betrifft eine Hubkolbenbrennkraftmaschine mit veränderlichem Verdich- tungsverhältnis, welche einen Exzenter umfasst, an dem ein Nebenpleuel angelenkt ist, der über einen Zwischenhebel mit einer Kurbelwelle sowie mit einem Pleuel zusammenwirkt, wobei der letztgenannte Pleuel an einem Kolben der Brennkraftmaschine schwenkbar gelagert ist. The invention relates to a reciprocating internal combustion engine with variable Verdich- ratio, which comprises an eccentric on which a Nebenpleuel is articulated, which interacts via an intermediate lever with a crankshaft and a connecting rod, the latter connecting rod is pivotally mounted on a piston of the internal combustion engine.
Eine derartige Hubkolbenbrennkraftmaschine ist beispielsweise aus der Such a reciprocating internal combustion engine is for example from the
WO 2007/057149 A1 bekannt. Ein Zwischenhebel dieser Hubkolbenbrennkraftmaschine, welche ein veränderliches Verdichtungsverhältnis aufweist, ist als Querhebel bezeichnet. Der Querhebel ist an drei Stellen gelenkig mit weiteren Komponenten der Hubkolbenbrennkraftmaschine gekoppelt. Hierbei handelt es sich um Verbindungen zu einem Nebenpleuel, einem Hubzapfen einer Kurbelwelle, sowie einem Pleuel, welcher im Fall der WO 2007/057149 A1 als Pleuelstange bezeichnet ist. Die an einem Kolben der Brennkraftmaschine angelenkte Pleuelstange ist also mit der Kurbelwelle nicht direkt, sondern über den Querhebel gekoppelt. Das vom Querhebel entfernte Ende des Nebenpleuels ist mit Hilfe eines Exzenters verstellbar. Die verschiedenen Dreh- und Gelenkpunkte sowie Schwerpunkte der einzelnen Elemente der bekannten Hubkolbenbrennkraftmaschine mit veränderlichem Verdichtungsverhältnis sollen derart anordenbar sein, dass Trägheits- und Fliehkräfte, die beim Bewegen der einzelnen Elemente entstehen, sich derart überlagern, dass sie sich zumindest teilweise gegenseitig aufheben. Die Hubkolbenbrennkraftmaschine kann in Vierzylinder-Bauart aus- geführt sein. WO 2007/057149 A1. An intermediate lever of this reciprocating internal combustion engine, which has a variable compression ratio, is referred to as a transverse lever. The transverse lever is articulated at three points with other components of the reciprocating internal combustion engine. These are connections to a Nebenpleuel, a crankpin of a crankshaft, and a connecting rod, which is referred to in the case of WO 2007/057149 A1 as a connecting rod. The hinged to a piston of the engine connecting rod is thus not coupled directly to the crankshaft, but via the cross lever. The remote from the cross lever end of Nebenpleuels is adjustable by means of an eccentric. The various rotational and pivot points and centers of gravity of the individual elements of the known reciprocating internal combustion engine with variable compression ratio should be such that inertial and centrifugal forces that arise when moving the individual elements, superimpose such that they cancel each other at least partially. The reciprocating internal combustion engine can be designed in four-cylinder design.
Eine weitere Hubkolbenbrennkraftmaschine mit einstellbarem Verdichtungsverhältnis ist zum Beispiel aus der DE 10 2009 000 772 A1 bekannt. In diesem Fall ist die Verstellung eines Exzenters mittels einer Zahnstange vorgesehen. Eine Exzenter-Verstellung in einem Kurbeltrieb einer Brennkraftmaschine mit variabler Verdichtung ist des Weiteren in der EP 1 154 134 A2 offenbart. Weitere Beispiele von Mechanismen, die die Verstellung des Verdichtungsverhältnisses von Hubkolben- brennkraftmaschinen ermöglichen, sind zum Beispiel in der EP 1 307 642 B1 be- schrieben. Another reciprocating internal combustion engine with adjustable compression ratio is known for example from DE 10 2009 000 772 A1. In this case, the adjustment of an eccentric means of a rack is provided. An eccentric adjustment in a crank mechanism of a variable compression internal combustion engine is further disclosed in EP 1 154 134 A2. Further examples of mechanisms which enable the adjustment of the compression ratio of reciprocating internal combustion engines are described, for example, in EP 1 307 642 B1.
Die DE 10 2010 032 427 A1 offenbart eine Stelleinrichtung für eine Hubkolbenmaschine mit variabler Verdichtung, welche als hydraulische Stelleinrichtung ausgebildet ist. Im Fall einer aus der WO 2008/148948 A2 bekannten Vorrichtung ist zur Verstel- lung des Verdichtungsverhältnisses einer Brennkraftmaschine ein elektrohydraulischer Aktor vorgesehen. DE 10 2010 032 427 A1 discloses an adjusting device for a reciprocating piston engine with variable compression, which is designed as a hydraulic adjusting device. In the case of a device known from WO 2008/148948 A2, an electrohydraulic actuator is provided for adjusting the compression ratio of an internal combustion engine.
Allgemein haben Hubkolbenbrennkraftmaschinen mit variablem Verdichtungsverhältnis gegenüber Hubkolbenbrennkraftmaschine mit konstantem Verdichtungsverhältnis den Vorteil, dass sie bei niedriger Last mit hohem Verdichtungsverhältnis und damit besonders verbrauchsgünstig und im Fall hoher Leistungsanforderung mit abgesenktem Verdichtungsverhältnis und gleichzeitiger Aufladung, typischerweise Turboaufladung, betrieben werden können. Generally, variable compression ratio reciprocating internal combustion engines have a constant compression ratio reciprocating internal combustion engine having the advantage that they can be operated at low load with high compression ratio, and thus particularly fuel efficient and in the case of high power demand with reduced compression ratio and simultaneous boost, typically turbocharging.
Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolbenbrennkraftmaschine mit veränderlichem Verdichtungsverhältnis anzugeben, welche sich gegenüber dem genannten Stand der Technik durch ein besonders günstiges Verhältnis zwischen langfristiger Robustheit, mechanischer Präzision und fertigungstechnischem Aufwand auszeichnet. The invention has for its object to provide a reciprocating internal combustion engine with variable compression ratio, which is distinguished from the cited prior art by a particularly favorable ratio between long-term robustness, mechanical precision and manufacturing effort.
Diese Aufgabe wird erfindungsgemäß gelöst durch eine Hubkolbenbrennkraftmaschine mit den Merkmalen des Anspruchs 1 . Es handelt sich hierbei um eine Hubkolbenbrennkraftmaschine mit veränderlichem Verdichtungsverhältnis, die in an sich bekanntem Grundaufbau einen Exzenter umfasst, an welchem ein Nebenpleuel angelenkt ist, welcher andererseits über einen Zwischenhebel mit der Kurbelwelle der Brennkraftmaschine sowie mit einem an einem Kolben der Brennkraftmaschine gelagerten Pleu- el zusammenwirkt. Erfindungsgemäß ist zur Verstellung des Exzenters ein Linearantrieb vorgesehen, der über ein Verstellpleuel mit einem Verstellarm des Exzenters gekoppelt ist. Der Linearantrieb ermöglicht eine Betätigung des Exzenters mit moderaten Kräften bei zugleich sehr guter mechanischer Präzision. This object is achieved by a reciprocating internal combustion engine having the features of claim 1. This is a reciprocating internal combustion engine with variable compression ratio, which comprises an eccentric in a known basic structure, to which a Nebenpleuel is hinged, on the other hand via an intermediate lever with the crankshaft of the internal combustion engine and with a mounted on a piston of the internal combustion engine Pleu- el interacts. According to the invention, a linear drive is provided for adjusting the eccentric, which is coupled via a Verstellpleuel with an adjustment of the eccentric. The linear drive allows the eccentric to be operated with moderate forces and at the same time with very good mechanical precision.
In bevorzugter Ausgestaltung handelt es sich bei dem Linearantrieb um einen Gewindetrieb. Gewindetriebe sind sowohl spielarm auslegbar als auch rationell herstellbar. In a preferred embodiment, the linear drive is a screw drive. Screw drives are both low-play interpretable and rational to produce.
Gemäß einer ersten Variante ist der Gewindetrieb selbsthemmend ausgeführt. Dies bedeutet, dass der Gewindetrieb nicht betätigbar ist, indem durch das Verstellpleuel eine Kraft in ihn eingeleitet wird. Der selbsthemmende Gewindetrieb kann ein einfaches Bewegungsgewinde aufweisen. Das heißt, dass die Spindelmutter des Gewindetriebs unmittelbar, ohne Zwischenschaltung von Wälzkörpern, mit der Gewindespindel zusammenwirkt. Die Selbsthemmung des Gewindetriebs ist gleichbedeutend damit, dass ein einmal eingestelltes Verdichtungsverhältnis der Hubkolbenbrennkraftmaschi- ne ohne Energieversorgung des Linearantriebs konstant bleibt. According to a first variant, the screw is self-locking. This means that the screw is not operable by a force is introduced through the Verstellpleuel. The self-locking screw drive can have a simple movement thread. This means that the spindle nut of the screw drive cooperates directly with the threaded spindle without the interposition of rolling elements. The self-locking of the screw drive is synonymous with the fact that once a compression ratio of the Hubkolbenbrennkraftmaschi- ne remains constant without power supply of the linear drive.
Gemäß einer zweiten Variante ist der Gewindetrieb, welcher zur Verstellung des Exzenters vorgesehen ist, nicht selbsthemmend ausgeführt. In diesem Fall handelt es sich bei dem Gewindetrieb vorzugsweise um einen Kugelgewindetrieb oder einen sonstigen Wälzgewindetrieb, welcher Wälzkörper beispielsweise Rollen, zwischen Gewindespindel und Spindelmutter aufweist. Die fehlende Selbsthemmung des Gewindetriebs hat den Vorteil, dass bei einem Ausfall der Energieversorgung des Linearantriebs der Exzenter selbsttätig eine Vorzugsstellung einnehmen kann, was mit ei- ner Normal-Einstellung des Verdichtungsverhältnisses einhergeht. According to a second variant of the screw, which is provided for adjusting the eccentric, not designed to be self-locking. In this case, the screw drive is preferably a ball screw or other Wälzgewindetrieb, which has rolling elements, for example, rollers, between the threaded spindle and the spindle nut. The lack of self-locking of the screw drive has the advantage that in case of failure of the power supply of the linear drive of the eccentric can automatically assume a preferred position, which is associated with a normal setting of the compression ratio.
Die Steigung eines nicht selbsthemmenden Gewindetriebes ist typischerweise größer als die Steigung eines selbsthemmenden Gewindetriebs. Unter diesem Aspekt wären zur Betätigung des nicht selbsthemmenden Gewindetriebs im Vergleich zum selbsthemmenden Gewindetrieb höhere Antriebsmomente erforderlich, was jedoch durch die reibungstechnisch günstigeren Eigenschaften des nicht selbsthemmenden Gewin- detriebs teilweise ausgeglichen oder sogar überkompensiert wird. Für hohe Verstellgeschwindigkeiten ist der nicht selbsthemmende Gewindetrieb besonders geeignet. Dagegen zeichnet sich der selbsthemmende Gewindetrieb dadurch aus, dass beim Betrieb der Hubkolbenbrennkraftmaschine geringere oder sogar keinerlei Haltern o- mente, welche den Linearantrieb in konstanter Position halten, erforderlich sind. Aufgrund der gegebenen Übersetzungsverhältnisse von Gewindetrieben ist sowohl im Fall eines selbsthemmenden Gewindetriebs als auch im Fall eines nicht selbsthemmenden Gewindetriebs eine stoßartige Belastung auf den Kurbeltrieb der Hubkolbenbrennkraftmaschine ohne praktische Bedeutung für die Stabilität, Präzision und Lang- lebigkeit des Linearantriebs, welcher über den Verstellpleuel eine Verschwenkung des Verstellarms des Exzenters ermöglicht. The pitch of a non-self-locking screw drive is typically greater than the pitch of a self-locking screw drive. In this aspect, higher drive torques would be required to operate the non-self-locking screw drive compared to the self-locking screw drive, but this is due to the lower friction properties of the non-self-locking screw drive. partially compensated or even overcompensated. For high adjustment speeds, the non-self-locking screw drive is particularly suitable. By contrast, the self-locking screw drive is characterized by the fact that during operation of the reciprocating internal combustion engine, lower or even no holding elements, which hold the linear drive in a constant position, are required. Due to the given gear ratios of screw drives, both in the case of a self-locking screw drive and in the case of a non-self-locking screw drive a shock load on the crank mechanism of the reciprocating internal combustion engine without practical significance for the stability, precision and longevity of the linear drive, which pivoting on the Verstellpleuel allows the adjustment of the eccentric.
Der Verstellarm des Exzenters ist vorzugsweise über einen Winkel von mehr als 90° verschwenkbar. Der Verstellarm bildet zusammen mit dem Verstellpleuel und dem Li- nearantrieb ein primäres Stellgetriebe in Form eines Schubkurbelgetriebes, dem ein sekundäres Stellgetriebe nachgeschaltet ist, das letztlich den Kolben der Brennkraftmaschine verstellt. Das sekundäre Stellgetriebe umfasst den Exzenter, den Zwischenhebel und den Pleuel, welcher an dem den Brennraum begrenzenden Kolben der Brennkraftmaschine gelagert ist. Die beiden Stellgetriebe weisen spezifische Drehmomentübertragungsfunktionen auf. Jede Drehmomentübertragungsfunktion gibt dabei das Verhältnis zwischen eingeleitetem Drehmoment und Abtriebsdrehmoment des jeweiligen Stellgetriebes an. In bevorzugter Ausgestaltung weisen die Drehmomentübertragungsfunktionen beider Stellgetriebe im gesamten Verstellbereich von vorzugsweise mehr als 90 °, bezogen auf den Einstellwinkel des Verstellarms, entge- gengesetzte Krümmungen auf. Beispielsweise weist die Drehmomentübertragungsfunktion des primären Stellgetriebes ein einziges Maximum und die Drehmomentübertragungsfunktion des sekundären Stellgetriebes ein einziges Minimum auf, wobei die Extremwerte der beiden Drehmomentübertragungsfunktionen etwa in der Mitte des Verstellbereichs liegen. The adjustment of the eccentric is preferably pivotable over an angle of more than 90 °. The adjustment together with the Verstellpleuel and the linear drive a primary actuating mechanism in the form of a sliding-crank mechanism, which is followed by a secondary actuating mechanism, which ultimately adjusts the piston of the internal combustion engine. The secondary actuating mechanism comprises the eccentric, the intermediate lever and the connecting rod, which is mounted on the combustion chamber limiting piston of the internal combustion engine. The two actuating gears have specific torque transfer functions. Each torque transfer function indicates the ratio between the introduced torque and the output torque of the respective adjusting gear. In a preferred embodiment, the torque transmission functions of both control gears in the entire adjustment range of preferably more than 90 °, based on the setting angle of the adjustment, opposite curvatures. For example, the torque transmitting function of the primary actuating gear has a single maximum and the torque transmitting function of the secondary actuating gear a single minimum, wherein the extreme values of the two torque transmitting functions are approximately in the middle of the adjustment.
Die Hintereinanderschaltung der beiden Stellgetriebe sorgt dafür, dass eine resultierende Gesamtdrehmomentübertragungsfunktion, welche das Verhältnis zwischen der Kraft, die am Ausgang des sekundären Stellgetriebes erzeugt wird, und dem hierfür erforderlichen Antriebsmoment des Linearantriebs angibt, eine geringere Übersetzungsbandbreite als jede der beiden einzelnen Drehmomentübertragungsfunktionen aufweist. Insbesondere sind Ausführungsformen realisierbar, bei denen das Verhältnis zwischen erzeugter Kraft am Ausgang des sekundären Stellgetriebes und Antriebsmoment, welches in die Eingangsseite des primären Stellgetriebes eingeleitet wird, über den gesamten Verstellbereich zumindest annähernd konstant ist. The series connection of the two adjusting gears ensures that a resulting total torque transfer function, which is the ratio between the Force, which is generated at the output of the secondary actuating gear, and the required drive torque of the linear drive indicates that has a lower translation bandwidth than each of the two individual torque-transmitting functions. In particular, embodiments are feasible in which the ratio between generated force at the output of the secondary actuating gear and drive torque, which is introduced into the input side of the primary adjusting gear, over the entire adjustment range is at least approximately constant.
Der Linearantrieb, welcher der Verstellung des Exzenters dient, ist vorzugsweise elektrisch angetrieben. Prinzipiell ist auch ein sonstiger, beispielsweise hydraulischer, Antrieb des zur Verschwenkung des Verstellarms des Exzenters vorgesehenen Linearantriebs möglich. The linear drive, which serves to adjust the eccentric, is preferably driven electrically. In principle, another, for example hydraulic, drive of the provided for pivoting the adjustment of the eccentric linear drive is possible.
Nachfolgend wird ein Ausführungsbeispiel der Erfindung anhand einer Zeichnung nä- her erläutert. Hierin zeigen, teilweise grob schematisiert: An exemplary embodiment of the invention will be explained in greater detail below with reference to a drawing. Herein show, partly roughly schematized:
Fig. 1 ausschnittsweise einen Verstellmechanismus zur Veränderung des Verdichtungsverhältnisses einer Brennkraftmaschine, 1 shows a detail of an adjusting mechanism for changing the compression ratio of an internal combustion engine,
Fig. 2 ein Detail aus der Anordnung nach Fig. 1 , FIG. 2 shows a detail from the arrangement according to FIG. 1, FIG.
Fig. 3 eine Drehmomentübertragungsfunktion eines primären Stellgetriebes des Verstellmechanismus, 3 shows a torque transmission function of a primary adjusting gear of the adjusting mechanism,
Fig. 4 eine Drehmomentübertragungsfunktion eines sekundären Stellgetriebes des Verstellmechanismus, 4 shows a torque transfer function of a secondary adjusting gear of the adjusting mechanism,
Fig. 5 eine resultierende Gesamtdrehmomentübertragungsfunktion des Verstellmechanismus, den Zusammenhang zwischen Steigung eines Gewindes und Wirkungs grad des Verstellmechanismus, 5 shows a resulting total torque transfer function of the adjustment mechanism, the relationship between the pitch of a thread and the degree of efficiency of the adjusting mechanism,
die beiden miteinander gekoppelten Stellgetriebe des Verstellmechanismus in einem ersten Betriebszustand, the two mutually coupled actuating mechanism of the adjusting mechanism in a first operating state,
ausschnittsweise die Anordnung nach Fig. 7 in einem zweiten Betriebszustand, 1 in a second operating state,
ausschnittsweise die Anordnung nach Fig. 7 in einem dritten Betriebszu stand. partially the arrangement of FIG. 7 in a third Betriebszu stood.
Die Figuren 1 und 2 sowie die Figuren 7, 8, 9 zeigen in verschiedenen, nicht maßstäb- liehen Darstellungen Merkmale eines insgesamt mit dem Bezugszeichen 1 gekennzeichneten Verstellmechanismus zur Variation des Verdichtungsverhältnisses einer Hubkolbenbrennkraftmaschine, beispielsweise in Form eines Mehrzylinder- Reihenmotors. Hinsichtlich der grundsätzlichen Funktion des Verstellmechanismus 1 wird auf den eingangs zitierten Stand der Technik verwiesen. Figures 1 and 2 and Figures 7, 8, 9 show in various, not to scale lent illustrations features of a generally designated by the reference numeral 1 adjusting mechanism for varying the compression ratio of a reciprocating internal combustion engine, for example in the form of a multi-cylinder in-line engine. With regard to the basic function of the adjusting mechanism 1, reference is made to the cited prior art.
Der Verstellmechanismus 1 ist aus zwei hintereinander geschalteten Stellgetrieben 2, 3, nämlich einem primären Stellgetriebe 2 und einem sekundären Stellgetriebe 3, aufgebaut. Gemeinsames Element beider Stellgetriebe 2, 3 ist ein Exzenter 4, wobei eine Verschwenkung des Exzenters 4 durch einen Verstellarm 5, der dem primären Stell- getriebe 2 zuzurechnen ist, möglich ist. Am Exzenter 4 ist ein Nebenpleuel 6 angelenkt, welcher gelenkig mit einem Zwischenhebel 7 gekoppelt ist. Der Zwischenhebel 7 weist eine dreieckige Grundform auf und ist mit einer Kurbelwelle 8 an einem Kurbelzapfen 9 gekoppelt. An einem mit 10 bezeichneten Pleuelanlenkpunkt des Zwischenhebels 7, welcher die dritte Ecke des Zwischenhebels 7 darstellt, ist ein Pleuel 1 1 angelenkt. Der Pleuelanlenkpunkt 10 wird auch als unteres Pleuellager bezeichnet. Ein oberes Pleuellager ist mit 12 bezeichnet und stellt die Verbindung zu einem Kolben 13 der Brennkraftmaschine her. Die Bezeichnungen„unteres" und„oberes" Pleuellager implizieren keine Aussage über die Einbaulage. The adjusting mechanism 1 is composed of two actuators 2, 3 connected in series, namely a primary actuating gear 2 and a secondary actuating gear 3. A common element of both control gear 2, 3 is an eccentric 4, wherein a pivoting of the eccentric 4 by an adjustment 5, which is attributable to the primary control gear 2, is possible. On the eccentric 4 a Nebenpleuel 6 is hinged, which is pivotally coupled to an intermediate lever 7. The intermediate lever 7 has a triangular basic shape and is coupled to a crankshaft 8 on a crank pin 9. At a designated Pleuelanlenkpunkt of the intermediate lever 7, which represents the third corner of the intermediate lever 7, a connecting rod 1 1 is articulated. The Pleuelanlenkpunkt 10 is also referred to as a lower connecting rod bearing. An upper connecting rod bearing is denoted by 12 and establishes the connection to a piston 13 of the internal combustion engine. The terms "lower" and "upper" connecting rod bearings do not imply any statement about the installation position.
Die Schwenkachse, um welche der Verstellarm 5 schwenkbar ist, ist mit SW bezeichnet. Der entsprechende Verstellwinkel (Fig. 3, 4, 5) ist mit V und der gesamte Verstellbereich des Verstellarms 5 mit VB bezeichnet. The pivot axis about which the adjustment arm 5 is pivotable is designated SW. The corresponding adjustment angle (FIGS. 3, 4, 5) is designated V and the entire adjustment range of the adjustment arm 5 is VB.
Der Verstellarm 5 ist mit einem Verstellpleuel 14 gekoppelt, welcher an einem ersten Verstellpleuellagerpunkt 15 des Verstellarms 5 angelenkt ist. Ein zweiter Verstellpleu- ellagerpunkt 16 stellt eine gelenkige Verbindung zwischen dem Verstellpleuel 14 und einer Spindelmutter 17 her. Die Spindelmutter 17 ist Teil eines Linearantriebs 18, weicher weiter eine Gewindespindel 19 aufweist und als Kugelgewindetrieb ausgebildet ist. Die Gewindespindel 19 ist mit Hilfe zweier Wälzlager 20, 21 drehbar gelagert; die Spindelmutter 17 ist ausschließlich verschiebbar. Zum Antrieb der Gewindespindel 19 ist ein Elektromotor 22 vorgesehen. The adjustment 5 is coupled to a Verstellpleuel 14 which is articulated to a first Verstellpleuellagerpunkt 15 of the adjustment 5. A second adjusting splined 16 provides an articulated connection between the Verstellpleuel 14 and a spindle nut 17. The spindle nut 17 is part of a linear drive 18, softer further comprises a threaded spindle 19 and is designed as a ball screw. The threaded spindle 19 is rotatably supported by means of two rolling bearings 20, 21; the spindle nut 17 is exclusively displaceable. To drive the threaded spindle 19, an electric motor 22 is provided.
Der maximale Verschiebebereich der Spindelmutter 17 ist auf den Verstellbereich VB des Verstellarms 5 abgestimmt. In Fig. 2 angedeutete, mit TP bezeichnete Totpunkte des Verstellarms 5 werden in keinem Betriebszustand des Verstellmechanismus 1 erreicht. Eine in Fig. 3 skizzierte erste Drehmomentübertragungsfunktion MDI stellt das Verhältnis zwischen dem im Verstellarm 5, das heißt am Ausgang des primären Stellgetriebes 2, wirkenden Drehmoment und dem vom Elektromotor 22 aufgebrachten und damit in der Gewindespindel 19 wirkenden Drehmoment in Abhängigkeit vom Verstellwinkel V dar. Die Drehmomentübertragungsfunktion MDI beschreibt eine Kurve mit einer Krümmung, die über den gesamten Verstellbereich VB das identische Vorzeichen aufweist. In der mit M bezeichneten Mittelstellung des Verstellarms 5 (entsprechend Fig. 8) weist die Drehmomentübertragungsfunktion MDI ein Maximum auf. An den Rändern des Verstellbereichs VB (Fig. 7, Fig. 9) ist die Drehmomentübertra- gungsfunktion MDI minimal. ln einer Darstellung analog Fig. 3 zeigt Fig. 4 die mit MD2 bezeichnete Drehmomentübertragungsfunktion des sekundären Stellgetriebes 3. In diesem Fall befindet sich ein einziges Minimum im Bereich der Mittelstellung M des Verstellarms 5, während die Drehmomentübertragungsfunktion MD2 an den Rändern des Verstellbereichs VB ma- ximal ist. The maximum displacement range of the spindle nut 17 is matched to the adjustment range VB of the adjustment arm 5. In Fig. 2 indicated, designated TP dead centers of Verstellarms 5 are achieved in any operating condition of the adjusting mechanism 1. A first torque transfer function MDI outlined in FIG. 3 represents the relationship between the torque acting in the adjusting arm 5, that is, at the output of the primary adjusting gear 2, and the torque applied by the electric motor 22 and thus acting in the threaded spindle 19 as a function of the adjusting angle V. The torque transfer function MDI describes a curve with a curvature that has the same sign over the entire adjustment range VB. In the middle position of the adjustment arm 5 (corresponding to FIG. 8) designated M, the torque transfer function MDI has a maximum. At the edges of the adjustment range VB (FIGS. 7, 9), the torque transfer function MDI is minimal. In an illustration analogous to FIG. 3, FIG. 4 shows the torque transmission function of the secondary adjusting gear 3 designated MD2. In this case, a single minimum is in the region of the center position M of the adjusting arm 5, while the torque transmitting function MD2 is located at the edges of the adjusting range VB. is ximal.
Eine mit MDG bezeichnete Gesamtdrehmomentübertragungsfunktion, welche in Fig. 5 idealisiert dargestellt ist, ist das Resultat der Hintereinanderschaltung von primärem Stellgetriebe 2 und sekundärem Stellgetriebe 3. Wie anschaulich aus Fig. 5 hervor- geht, ist das zur Betätigung des Verstellmechanismus 1 vom Elektromotor 2 aufzubringende Drehmoment über den gesamten Verstellbereich VB praktisch konstant. A total torque transmission function denoted MDG, which is illustrated in an idealized manner in FIG. 5, is the result of the series connection of the primary actuating gear 2 and the secondary actuating gear 3. As clearly shown in FIG. 5, this is to be applied by the electric motor 2 for actuating the adjusting mechanism 1 Torque over the entire adjustment range VB practically constant.
Die Ausbildung des Linearantriebs 18 als nicht selbsthemmender Gewindetrieb ist gleichbedeutend damit, dass dessen Wirkungsgrad η größer als 50 % ist. Die mit St bezeichnete Steigung der Gewindespindel 19 sowie der Spindelmutter 17 ist größer als bei typischen, im Maschinenbau verwendeten Schraubengeometrien. Bezogen auf das Diagramm nach Fig. 6 bedeutet dies, dass sowohl die Steigung St als auch der Wirkungsgrad η des Linearantriebs 18 im oberen Bereich liegen. Bei einem abgewandelten Linearantrieb 18, welcher ebenfalls für die Verschwenkung des Verstellarms 5 nutzbar ist, kann eine Steigung St im unteren Bereich gewählt werden, welche mit einem deutlich verminderten Wirkungsgrad η einhergeht, wie aus Fig. 6 ersichtlich ist, wobei in diesem Fall Wälzkörper im Linearantrieb 18 entfallen, das heißt ein einfaches Bewegungsgewinde vorliegt. Mit dieser modifizierten Gestaltung des Linearantriebs 18 ist das primäre Stellgetriebe 2 als selbsthemmendes Getriebe ausgebildet. Bezuqszeichenliste Verstellmechanismus The design of the linear drive 18 as a non-self-locking screw drive is synonymous with the fact that its efficiency η is greater than 50%. The slope of the threaded spindle 19 and of the spindle nut 17, designated St, is greater than in typical screw geometries used in mechanical engineering. With reference to the diagram of FIG. 6, this means that both the slope St and the efficiency η of the linear drive 18 are in the upper range. In a modified linear drive 18, which is also used for the pivoting of the adjusting 5, a slope St can be selected in the lower region, which is associated with a significantly reduced efficiency η, as shown in FIG. 6 can be seen, in which case rolling elements in Linear actuator 18 omitted, that is, a simple motion thread exists. With this modified design of the linear drive 18, the primary actuating gear 2 is designed as a self-locking gear. Reference character list adjustment mechanism
primäres Stellgetriebe primary actuating gear
sekundäres Stellgetriebe secondary actuating gear
Exzenter eccentric
Verstellarm adjusting arm
Nebenpleuel auxiliary connecting rod
Zwischenhebel intermediate lever
Kurbelwelle crankshaft
Kurbelzapfen crank pin
10 Pleuelanlenkpunkt 10 connecting rod connection point
1 1 Pleuel 1 1 connecting rod
12 Pleuellager 12 connecting rod bearings
3 Kolben 3 pistons
14 Verstellpleuel 14 adjustable connecting rods
15 Verstellpleuellagerpunkt 15 adjustable baffle bearing point
16 Verstellpleuellagerpunkt 16 Adjustable brake bearing point
17 Spindelmutter 17 spindle nut
18 Linearantrieb 18 linear drive
19 Gewindespindel 19 threaded spindle
20 Wälzlager 20 rolling bearings
21 Wälzlager 21 rolling bearings
22 Elektromotor η Wirkungsgrad 22 electric motor η efficiency
TP Totpunkt TP dead center
VB Verstellbereich VB adjustment range
V Verstellwinkel V adjustment angle
M Mittelstellung M middle position
St Steigung St slope
SW Schwenkachse SW swivel axis
MD-I , MD2, MDG Drehmomentübertragungsfunktionen MD-I, MD2, MDG torque transfer functions
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016201035.2 | 2016-01-26 | ||
| DE102016201035.2A DE102016201035A1 (en) | 2016-01-26 | 2016-01-26 | Reciprocating internal combustion engine with variable compression ratio |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2017129175A1 true WO2017129175A1 (en) | 2017-08-03 |
Family
ID=58046429
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/DE2017/100044 Ceased WO2017129175A1 (en) | 2016-01-26 | 2017-01-24 | Reciprocating piston internal combustion engine having a variable compression ratio |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE102016201035A1 (en) |
| WO (1) | WO2017129175A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112639266A (en) * | 2018-11-14 | 2021-04-09 | 宝马股份公司 | Device for changing compression ratio, reciprocating piston internal combustion engine and working device |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1154134A2 (en) | 2000-05-09 | 2001-11-14 | Nissan Motor Company, Limited | Variable compression ratio mechanism for reciprocating internal combustion engine |
| EP1197647A2 (en) * | 2000-10-12 | 2002-04-17 | Nissan Motor Co., Ltd. | Variable compression ration mechanism for reciprocating internal combustion engine |
| EP1307642B1 (en) | 2000-08-08 | 2004-05-19 | DaimlerChrysler AG | Internal combustion piston engine comprising various compression influences |
| EP1496219A1 (en) * | 2003-07-08 | 2005-01-12 | HONDA MOTOR CO., Ltd. | Variable compression ratio engine |
| DE102005020270A1 (en) * | 2005-04-30 | 2006-11-09 | Daimlerchrysler Ag | Internal combustion engine with variable compression ratio |
| WO2007057149A1 (en) | 2005-11-17 | 2007-05-24 | Daimler Ag | Reciprocating-piston internal combustion engine with variable compression ratio |
| WO2008148948A2 (en) | 2007-04-16 | 2008-12-11 | Vianney Rabhi | Hydroelectric device for closed-loop driving the control jack of a variable compression rate engine |
| EP2022959A2 (en) * | 2007-08-10 | 2009-02-11 | Nissan Motor Company Limited | Variable compression ratio device for internal combustion engine |
| EP2055914A2 (en) * | 2007-10-29 | 2009-05-06 | Nissan Motor Co., Ltd. | Multi-link variable compression ratio engine |
| JP2009209690A (en) * | 2008-02-29 | 2009-09-17 | Nissan Motor Co Ltd | Variable compression ratio internal combustion engine |
| DE102009000772A1 (en) | 2009-02-11 | 2010-08-12 | Zf Friedrichshafen Ag | Compression ratio adjusting device for reciprocating internal combustion engine of vehicle, has eccentric shaft rotated to change effective connecting rod length, and linear motor provided for driving eccentric shaft |
| DE102010032427A1 (en) | 2010-07-28 | 2012-02-02 | Daimler Ag | Actuating device for reciprocating piston engine of motor vehicle, comprises actuating portion, by which compression ratio of cylinder of reciprocating piston engine is variably adjustable corresponding to actuating device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014218405B3 (en) * | 2014-09-15 | 2015-11-05 | Schaeffler Technologies AG & Co. KG | Method for producing a spindle for a ball screw, as well as a spindle produced thereafter |
-
2016
- 2016-01-26 DE DE102016201035.2A patent/DE102016201035A1/en not_active Ceased
-
2017
- 2017-01-24 WO PCT/DE2017/100044 patent/WO2017129175A1/en not_active Ceased
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1154134A2 (en) | 2000-05-09 | 2001-11-14 | Nissan Motor Company, Limited | Variable compression ratio mechanism for reciprocating internal combustion engine |
| EP1307642B1 (en) | 2000-08-08 | 2004-05-19 | DaimlerChrysler AG | Internal combustion piston engine comprising various compression influences |
| EP1197647A2 (en) * | 2000-10-12 | 2002-04-17 | Nissan Motor Co., Ltd. | Variable compression ration mechanism for reciprocating internal combustion engine |
| EP1496219A1 (en) * | 2003-07-08 | 2005-01-12 | HONDA MOTOR CO., Ltd. | Variable compression ratio engine |
| DE102005020270A1 (en) * | 2005-04-30 | 2006-11-09 | Daimlerchrysler Ag | Internal combustion engine with variable compression ratio |
| WO2007057149A1 (en) | 2005-11-17 | 2007-05-24 | Daimler Ag | Reciprocating-piston internal combustion engine with variable compression ratio |
| WO2008148948A2 (en) | 2007-04-16 | 2008-12-11 | Vianney Rabhi | Hydroelectric device for closed-loop driving the control jack of a variable compression rate engine |
| EP2022959A2 (en) * | 2007-08-10 | 2009-02-11 | Nissan Motor Company Limited | Variable compression ratio device for internal combustion engine |
| EP2055914A2 (en) * | 2007-10-29 | 2009-05-06 | Nissan Motor Co., Ltd. | Multi-link variable compression ratio engine |
| JP2009209690A (en) * | 2008-02-29 | 2009-09-17 | Nissan Motor Co Ltd | Variable compression ratio internal combustion engine |
| DE102009000772A1 (en) | 2009-02-11 | 2010-08-12 | Zf Friedrichshafen Ag | Compression ratio adjusting device for reciprocating internal combustion engine of vehicle, has eccentric shaft rotated to change effective connecting rod length, and linear motor provided for driving eccentric shaft |
| DE102010032427A1 (en) | 2010-07-28 | 2012-02-02 | Daimler Ag | Actuating device for reciprocating piston engine of motor vehicle, comprises actuating portion, by which compression ratio of cylinder of reciprocating piston engine is variably adjustable corresponding to actuating device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112639266A (en) * | 2018-11-14 | 2021-04-09 | 宝马股份公司 | Device for changing compression ratio, reciprocating piston internal combustion engine and working device |
| US11401859B2 (en) | 2018-11-14 | 2022-08-02 | Bayerische Motoren Werke Aktiengesellschaft | Device for varying a compression ratio, reciprocating-piston internal combustion engine and working device |
| CN112639266B (en) * | 2018-11-14 | 2023-02-17 | 宝马股份公司 | Devices for changing the compression ratio, reciprocating piston internal combustion engines and working equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102016201035A1 (en) | 2017-07-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE102011116952B4 (en) | Multi-joint crank drive of an internal combustion engine and method for operating a multi-joint crank drive | |
| DE10051271B4 (en) | In their compression ratio adjustable piston internal combustion engine with integrated Verstellaktuator | |
| WO2012143078A9 (en) | Device for changing a compression ratio of a reciprocating piston internal combustion engine | |
| WO2014019683A1 (en) | Hydraulic freewheel for an internal combustion engine with variable compression ratio | |
| WO2012069257A1 (en) | Apparatus for reducing the play in a gear mechanism | |
| EP2693079A2 (en) | Planetary gear mechanism and a handling device equipped with such a planetary gear | |
| DE102012113200A1 (en) | Variable compression ratio device | |
| WO2008052531A1 (en) | Adjustment drive for the local adjustment of a chassis component | |
| DE202014004439U1 (en) | Arrangement for driving an adjusting shaft for adjusting the expansion stroke and / or the compression ratio of an internal combustion engine | |
| WO2017129175A1 (en) | Reciprocating piston internal combustion engine having a variable compression ratio | |
| EP3267011A1 (en) | Device for changing a compression ratio of a reciprocating piston combustion engine | |
| WO2006117080A1 (en) | Adjusting apparatus for an internal combustion engine | |
| DE102013019214B3 (en) | Multi-joint crank drive of an internal combustion engine and method for operating a multi-joint crank drive | |
| DE102014012506B3 (en) | Method for operating a multi-link crank drive for an internal combustion engine and corresponding multi-joint crank drive | |
| DE102014201979B4 (en) | Arrangement for driving an adjusting shaft for adjusting the expansion stroke and/or the compression ratio of an internal combustion engine | |
| DE102014201981B4 (en) | Arrangement for driving an adjusting shaft for adjusting the expansion stroke and / or the compression ratio of an internal combustion engine | |
| DE102014015879B3 (en) | Method for operating an internal combustion engine and corresponding internal combustion engine | |
| DE102016003695B4 (en) | Method for operating an internal combustion engine with an actuating device for adjusting the actual compression ratio, and corresponding internal combustion engine | |
| DE102014018525B4 (en) | Multi-link crank drive for an internal combustion engine with fail-safe eccentric shaft locking device | |
| DE102014016866B3 (en) | Method for operating an internal combustion engine and corresponding internal combustion engine | |
| AT504322A1 (en) | SETTING DEVICE FOR POSITIONING A LOAD | |
| DE3317830C2 (en) | Fuel control device for a diesel engine | |
| DE102014201978B4 (en) | Arrangement for driving an adjusting shaft for adjusting the expansion stroke and / or the compression ratio of an internal combustion engine | |
| WO2012163382A1 (en) | Transmission device and adjusting device having such a transmission device | |
| DE102014015884B3 (en) | Multi-joint crank drive for a row cylinder block of an internal combustion engine and corresponding internal combustion engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17705297 Country of ref document: EP Kind code of ref document: A1 |
|
| 122 | Ep: pct application non-entry in european phase |
Ref document number: 17705297 Country of ref document: EP Kind code of ref document: A1 |