EP2792846A1 - Double crankshaft combustion engine - Google Patents
Double crankshaft combustion engine Download PDFInfo
- Publication number
- EP2792846A1 EP2792846A1 EP13002068.8A EP13002068A EP2792846A1 EP 2792846 A1 EP2792846 A1 EP 2792846A1 EP 13002068 A EP13002068 A EP 13002068A EP 2792846 A1 EP2792846 A1 EP 2792846A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- crankshaft
- crankshafts
- engine
- bearing
- synchronization gear
- 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.)
- Withdrawn
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
-
- 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
- F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
-
- 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
- F02B75/06—Engines with means for equalising torque
- F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
-
- 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
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
Definitions
- the invention relates to a double crankshaft internal combustion engine.
- Such devices are mainly used as compact energy sources, eg. As an outboard motor, as a drive for motorcycles or as an APU ("auxiliary power unit") in aviation. Due to the achievable smoothness they are also particularly suitable as "range extender” for vehicles with hybrid drive or for small combined heat and power plants.
- a double crankshaft motor which should allow a high specific power in a compact size and high smoothness, is for example in the document DE 103 48 345 B4 disclosed.
- a disadvantage of all these motors is that the compression ratio during operation can not be changed.
- the motors must therefore be designed for full-load operation, while in part-load operation, a higher compression would be readily acceptable, which in turn would achieve higher efficiency and lower consumption.
- Variable compression internal combustion engines are also known in the art. Such is in the document US 5,329,893 discloses an engine design in which the cylinder head and block are connected via a hinge to the crankcase, so that a small relative movement (eg 4 °) is made possible, which is controlled by a hydraulic actuator. Also in the publication US 2005/0028760 A1 a small relative movement between the cylinder block and crankcase is provided, controlled in this case by two rotating camshafts.
- the pamphlets WO 01/23722 A1 disclose engine designs in which the crankshaft bearings are designed to be height adjustable (for example, by eccentric), whereby the distance between the piston and cylinder head can be changed.
- EP 1 247 958 A1 such as WO 20081099018 A1 disclose engine designs in which, however, the storage of the connecting rods to the crank pin of the crankshaft is designed to be variable, for example, by eccentric sleeves, which are mounted controllably between crank pin and connecting rod eye.
- the object of the invention is to avoid the disadvantages of the prior art and in particular to enable variable compression in double crankshaft engines in everyday use.
- the motor can thus be designed so that no phase shift is set in the part-load range, where lower temperatures and pressures prevail.
- the piston is maximally raised in the partial load range and there is a maximum compression of the combustion mixture in the engine.
- the engine can be driven both in the part-load range and in the full load range at the limits of its capacity. It can thus be achieved over the entire load range of the engine, a higher compression compared to conventional engines.
- the utilization of the chemical energy of the fuel is better with higher compression.
- a higher utilization of the energy of the fuel and thus a lower fuel consumption can be achieved.
- Such an engine is suitable for mass production without any restrictions, since neither extreme complexity nor particularly tight manufacturing tolerances are required, which cause problems in other engine designs with variable compression and can cause, for example, high manufacturing costs.
- One of the two crankshafts carries a synchronization gear, which can rotate about the axis of the crankshaft. Furthermore, this crankshaft has a connecting element, which is displaceable along the axis of the crankshaft. Corresponding means for displacing the connecting element along the axis of the crankshaft are provided, which can press the connecting element against the synchronization gear.
- the connecting element has a ramp.
- the synchronization gear also has a ramp. The ramp of the connecting element and the ramp of the synchronization gear are arranged such that they engage positively with one another.
- the angular position of the synchronization gear on the crankshaft can be varied.
- each crankshaft has a synchronizing gear, wherein the two synchronization gears are engaged with each other to synchronize the two crankshafts.
- One of the two crankshafts in turn carries a synchronization gear which can rotate about the axis of the crankshaft. The angular position of this synchronization gear relative to this crankshaft can be varied hydraulically.
- area information always includes all - not mentioned - intermediate values and all imaginable subintervals.
- Fig. 1 shows a schematic cross section through a double crankshaft motor, as shown in EP 2 426 336 A2 is described.
- the two crankshafts 3 and 4 are synchronized with each other by means of the synchronization gears 1 and 2 and stored in the schematically indicated bearings 3a, 4a.
- the schematically indicated crank arm 15 terminates in a crank pin 14 and rotates synchronously with the synchronization gear 2.
- a corresponding crank pin 13 is formed on the synchronization gear 1.
- 14 engage connecting rods 5, 6.
- the two connecting rods 5, 6 end in pivot bearings 11 and 12, which are provided in the compensating element 7.
- the compensation element 7 resembles possibly existing game and slight desynchronization of the two crankshafts, as in EP 2 426 336 A2 described, out.
- the compensation element 7 is provided on the piston 8. This limits the combustion chamber 9 in the cylinder 10th
- a schematic cross-section is shown by a double crankshaft motor according to the invention, which in addition to the in EP 2 426 336 A2 Characteristics described also has means for phase shifting the two crankshafts 3 and 4 against each other. These means have set a phase shift in the figure by the angle ⁇ 2 . As a result, the left connecting rod 5 is lowered slightly. The compensating element 7 thereby tilts by the angle ⁇ 1 , thereby preventing the piston 8 from tilting. In addition, thereby the piston 8 is lowered relative to the situation with non-phase-shifted crankshafts. The compensation element 7 effectively averages the position of the both connecting rods 5 and 6, so that the effective top dead center is lowered.
- the combustion chamber 9 above the piston 8 is recognizable larger, the compression is reduced compared to the state with non-phase-shifted crankshafts.
- the means for phase shifting the two crankshafts are adjusted so that the angle ⁇ 2 is maximum at full load.
- Fig. 3 shows a diagram in which the kinematics of the double crankshaft drive is shown with and without phase shift and compared to a conventional engine with a crankshaft. All curves describe the distance of the small connecting rod eyes (upper bearing of the connecting rod) from the respectively associated crankshaft axis.
- the two dashed curves describe the two connecting rods of a double crankshaft engine, wherein the two crankshafts are phase-shifted by 20 ° from each other.
- the solid line describes the resulting (averaged) curve, measured in the center axis of the compensating element. It can be seen clearly that due to the phase shift, the effective stroke decreases.
- the dot-dashed curve describes the situation with a conventional engine with only one crankshaft. It can be seen clearly that the kinematics is a different, in particular, that in the double crankshaft motor, the up and down movements of the piston are different.
- Fig. 4 shows by way of example the additional piston stroke of a double crankshaft motor according to the invention as a function of the phase shift of the crankshafts against each other. It should be noted that the piston stroke is reduced by the phase shift. At maximum phase shift (in this example, this is 35 °), the piston stroke is minimal overall. The additional piston stroke is thus defined as zero in this case. Without phase shift (0 °), on the other hand, the piston stroke is maximum, which in this example means an additional 2.5 mm.
- Fig. 5 is exemplified the achieved compression ratio in a double crankshaft motor according to the invention as a function of the phase shift of the crankshafts against each other.
- the compression ratio varies between 25: 1 (phase shift 0 °) and 16: 1 (phase shift 35 °).
- the z under full load conditions. B. is limited to a compression of 16: 1, 9 points are obtained in the compression in the partial load range. This corresponds to a fuel saving of about 18%.
- Fig. 6 shows by way of example the thermal efficiency of a double crankshaft motor according to the invention in dependence on the phase shift of the crankshafts against each other. It can be clearly seen that the phase shift reduces the efficiency by lowering the compression ratio. This is acceptable in practical applications, since the maximum phase shift is conveniently done at full load conditions, the minimum phase shift, while allowing the best efficiency, is reserved for the part load operation, which is much more common and for longer periods in typical vehicle applications. For these situations, the efficiency is increased, in the present example by up to 20% (from 0.4 to 0.5).
- each crankshaft carries a synchronizing gear, the two synchronizing gears being engaged with each other to synchronize the two crankshafts.
- One of the two crankshafts 50 carries a synchronization gear 60, which is not fixed to the crankshaft 50 but can rotate about it. It can not be moved along the crankshaft 50.
- This synchronizing gear 60 is engaged with the synchronizing gear of the other crankshaft (not shown).
- At least one connecting element 70 is mounted on the crankshaft 50 such that it rotates with the crankshaft 50, but is displaceable in the longitudinal direction.
- Corresponding means 80 for displacing the connecting element 70 along the axis of the crankshaft 50 are provided, which can press the connecting element 70 against the synchronization gear 60 and thus firmly couple it to the rotation of the crankshaft 50.
- These means 80 may, for. B. be a hydraulic or electrical adjuster.
- Fig. 5 the hydraulic variant is shown schematically.
- the central oil hole 82 in the crankshaft 50 oil is promoted with a speed-dependent delivery pressure. If the speed increases, the pressure generated in the central oil bore 82 of the crankshaft and thus also in the hydraulic chamber 84 (in FIG Figure 5 only shown in section), which is connected via a feed line 86 with the central oil hole 82. Due to the pressure increase in the hydraulic chamber 84, the connecting element 70 is displaced in the direction of the synchronization gear 60 and this adjusted.
- the connecting element 70 has a ramp 90 at its end facing the synchronization gear 60.
- the synchronization gear 60 has a complementarily configured ramp 95.
- the two ramps 90, 95 are arranged such that they can engage positively with one another.
- the synchronization gear 60 is thus fixed in a more or less twisted position on the crankshaft 50, whereby compared to the other crankshaft, the synchronization gear is connected in a conventional manner with her, a phase shift is achieved ,
- a further embodiment of the means for phase shifting the crankshafts relative to one another is a vane-type adjuster, as in Fig. 8 shown in a section transverse to the crankshaft 50.
- the radially arranged hydraulic chambers 84 are supplied with oil via supply lines 86 from the central oil bore (not shown in this figure) of the crankshaft 50.
- the wing members 100 and the pins 102 of the synchronizing gear 60 are pushed apart. This results in a relative phase shift between the crankshaft 50 and the synchronization gear 60.
- An internal combustion engine is an internal combustion engine that converts chemical energy of a fuel into mechanical work by combustion. The combustion takes place in the combustion chamber, in which a mixture of fuel and ambient air is ignited. The thermal expansion of the hot gas is used to move a piston.
- internal combustion engines are the gasoline engine and the diesel engine, e.g. in automobiles.
- the double crankshaft engine is to be understood as phase shifting:
- the two crankshafts run in phase when the associated connecting rods of a cylinder each reach their highest position at the same time.
- the piston is then in its top dead center. If the two connecting rods of a cylinder reach their highest position at different times, then one connecting rod still has to cover one angle (which may be positive or negative) up to its highest position, when the other is in its highest position. This angle is the phase shift of the two crankshafts.
- the compression ratio is the ratio of the total cylinder space before compression to the remaining space after compression. With a higher compression ratio, the efficiency increases, but at the same time the tendency to knock increases in gasoline engines.
- the knocking can in turn be reduced by higher octane gasoline, optimization of the combustion chamber shape or the use of multiple spark plugs. As a rough guide to fuel economy, increasing the compression ratio by one point reduces fuel consumption by about 2%.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Es wird ein Doppelkurbelwellen-Verbrennungsmotor vorgeschlagen mit mindestens einem Zylinder, in dem ein Hubkolben hin- und herbewegbar angeordnet ist. Der Motor hat eine erste und eine zweite Kurbelwelle, wobei die beiden Kurbelwellen zueinander parallel verlaufen und sich gegensinnig synchron drehen. Dem Hubkolben sind ein erstes und ein zweites Pleuel zugeordnet, wobei das erste Pleuel mit seinem ersten Ende in einem ersten Schwenklager um eine erste Pleuelschwenkachse schwenkbar gelagert ist und mit seinem zweiten Ende an einem Kurbelzapfen der ersten Kurbelwelle drehbar gelagert ist. Entsprechendes gilt für das zweite Pleuel. Ferner ist am Hubkolben des Motors ein Lagerelement vorgesehen, das am Hubkolben um eine Lagerschwenkachse schwenkbar gelagert ist, die parallel zu den Pleuelschwenkachsen verläuft. Das erste und zweite Schwenklager sind an dem Lagerelement vorgesehen. Der Motor hat schließlich Mittel zur Phasenverschiebung der beiden Kurbelwellen gegeneinander. Dadurch lässt sich das Verdichtungsverhältnis im laufenden Betrieb variabel einstellen, ohne dass die Alltagstauglichkeit des Motors beeinträchtigt wird. Durch die variable Verdichtung wird eine erhebliche Kraftstoff-Einsparung erreicht.It is proposed a double crankshaft internal combustion engine with at least one cylinder in which a reciprocating piston is arranged back and forth. The engine has a first and a second crankshaft, wherein the two crankshafts are parallel to each other and rotate synchronously in opposite directions. The reciprocating piston is associated with a first and a second connecting rod, wherein the first connecting rod is pivotally mounted with its first end in a first pivot bearing about a first Pleuelschwenkachse and is rotatably mounted with its second end to a crank pin of the first crankshaft. The same applies to the second connecting rod. Further, a bearing element is provided on the reciprocating piston of the engine, which is mounted pivotably on the reciprocating piston about a bearing pivot axis which is parallel to the Pleuelschwenkachsen. The first and second pivot bearings are provided on the bearing member. The engine finally has means for phase shifting the two crankshafts against each other. As a result, the compression ratio can be adjusted variably during operation without impairing the everyday practicality of the engine. The variable compression achieves considerable fuel savings.
Description
Die Erfindung betrifft einen Doppelkurbelwellen-Verbrennungsmotor. Derartige Vorrichtungen dienen vorwiegend als kompakte Energiequellen, z. B. als Außenbordmotor, als Antrieb für Motorräder oder als APU ("auxiliary power unit") in der Luftfahrt. Aufgrund der erzielbaren Laufruhe eignen sie sich auch besonders als "range extender" für Fahrzeuge mit Hybridantrieb oder für kleine Blockheizkraftwerke.The invention relates to a double crankshaft internal combustion engine. Such devices are mainly used as compact energy sources, eg. As an outboard motor, as a drive for motorcycles or as an APU ("auxiliary power unit") in aviation. Due to the achievable smoothness they are also particularly suitable as "range extender" for vehicles with hybrid drive or for small combined heat and power plants.
Ein Doppelkurbelwellenmotor, der bei kompakten Abmessungen und hoher Laufruhe eine hohe spezifische Leistung ermöglichen soll, ist beispielsweise in der Druckschrift
In der Druckschrift
Nachteilig an allen diesen Motoren ist, dass das Verdichtungsverhältnis im laufenden Betrieb nicht verändert werden kann. Die Motoren müssen also für den Volllastbetrieb ausgelegt werden, während im Teillastbetrieb ohne weiteres eine höhere Verdichtung verkraftbar wäre, die ihrerseits einen höheren Wirkungsgrad und niedrigeren Verbrauch erzielen würde.A disadvantage of all these motors is that the compression ratio during operation can not be changed. The motors must therefore be designed for full-load operation, while in part-load operation, a higher compression would be readily acceptable, which in turn would achieve higher efficiency and lower consumption.
Verbrennungsmotoren mit variabler Verdichtung sind ebenfalls aus dem Stand der Technik bekannt. So ist in der Druckschrift
Die Druckschriften
Die Druckschriften
Alle diese Konstruktionen haben Probleme mit der Alltagstauglichkeit, da sie sehr kompliziert und/oder sehr wartungsintensiv sind.All of these designs have problems with everyday usability because they are very complicated and / or very maintenance intensive.
Aufgabe der Erfindung ist es, die Nachteile des Standes der Technik zu vermeiden und insbesondere variable Verdichtung bei Doppelkurbelwellenmotoren in alltagstauglicher Weise zu ermöglichen.The object of the invention is to avoid the disadvantages of the prior art and in particular to enable variable compression in double crankshaft engines in everyday use.
Diese Aufgabe wird durch die Erfindung mit den Merkmalen des unabhängigen Anspruchs gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet. Der Wortlaut sämtlicher Ansprüche wird hiermit durch Bezugnahme zum Inhalt dieser Beschreibung gemacht.This object is achieved by the invention with the features of the independent claim. Advantageous developments of the invention are characterized in the subclaims. The wording of all claims is hereby incorporated by reference into the content of this specification.
Vorgeschlagen wird ein Doppelkurbelwellen-Verbrennungsmotor mit:
- mindestens einem Zylinder, in dem ein Hubkolben hin- und herbewegbar angeordnet ist;
- einer ersten Kurbelwelle;
- einer zweiten Kurbelwelle;
- wobei die erste Kurbelwelle und die zweite Kurbelwelle zueinander parallel verlaufen und sich gegensinnig synchron drehen;
- wobei dem Hubkolben ein erstes und ein zweites Pleuel zugeordnet sind,
- wobei das erste Pleuel mit seinem ersten Ende in einem ersten Schwenklager um eine erste Pleuelschwenkachse schwenkbar gelagert ist und mit seinem zweiten Ende an einem Kurbelzapfen der ersten Kurbelwelle drehbar gelagert ist; und
- wobei das zweite Pleuel mit seinem ersten Ende in einem zweiten Schwenklager um eine zweite Pleuelschwenkachse schwenkbar gelagert ist und mit seinem zweiten Ende an einem Kurbelzapfen der zweiten Kurbelwelle drehbar gelagert ist; und mit
- einem Lagerelement;
- wobei das Lagerelement am Hubkolben um eine Lagerschwenkachse schwenkbar gelagert ist, die parallel zu den Pleuelschwenkachsen verläuft;
- wobei das erste und zweite Schwenklager an dem Lagerelement vorgesehen sind; und mit
- Mitteln zur Phasenverschiebung der beiden Kurbelwellen gegeneinander.
- at least one cylinder in which a reciprocating piston is arranged back and forth;
- a first crankshaft;
- a second crankshaft;
- wherein the first crankshaft and the second crankshaft are parallel to each other and rotate in opposite directions synchronously;
- wherein the reciprocating piston associated with a first and a second connecting rod,
- wherein the first connecting rod is pivotally mounted with its first end in a first pivot bearing about a first Pleuelschwenkachse and is rotatably mounted with its second end to a crank pin of the first crankshaft; and
- wherein the second connecting rod is pivotally mounted with its first end in a second pivot bearing about a second Pleuelschwenkachse and is rotatably mounted with its second end to a crank pin of the second crankshaft; and with
- a bearing element;
- wherein the bearing member is pivotally mounted on the reciprocating piston about a bearing pivot axis which is parallel to the Pleuelschwenkachsen;
- wherein the first and second pivot bearings are provided on the bearing member; and with
- Means for phase shift of the two crankshafts against each other.
Diese Mittel zur Phasenverschiebung der beiden Kurbelwellen gegeneinander ermöglichen es, den oberen Totpunkt des Hubkolbens abzusenken, wodurch das Volumen im Zylinder oberhalb des Hubraumes erhöht wird und das Verdichtungsverhältnis folglich abnimmt. Dies kann auch bei laufendem Motor erfolgen. Dabei bleibt die Alltagstauglichkeit und Belastbarkeit des Motors voll erhalten.These means for phase shifting the two crankshafts against each other make it possible to lower the top dead center of the reciprocating piston, whereby the volume in the cylinder is increased above the displacement and the compression ratio consequently decreases. This can also be done while the engine is running. The suitability for everyday use and the load capacity of the engine remain fully intact.
Mithilfe dieser Phasenverschiebung kann der Motor somit so ausgelegt werden, dass im Teillast-Bereich, wo geringere Temperaturen und Drücke herrschen, keine Phasenverschiebung eingestellt wird. Damit wird der Kolben im Teillastbereich maximal angehoben und es ergibt sich eine maximale Verdichtung des Verbrennungsgemisches im Motor.Using this phase shift, the motor can thus be designed so that no phase shift is set in the part-load range, where lower temperatures and pressures prevail. Thus, the piston is maximally raised in the partial load range and there is a maximum compression of the combustion mixture in the engine.
Erreicht der Motor hingegen höhere Drehzahlen oder gar seinen Volllast-Bereich, so kann im laufenden Betrieb eine Phasenverschiebung zwischen den beiden Kurbelwellen eingestellt werden. Daraus ergibt sich eine verringerte Verdichtung im Volllastbereich, die allerdings immer noch die Grenzen der Belastbarkeit des Motors erreichen kann.On the other hand, if the engine reaches higher speeds or even its full load range, a phase shift between the two crankshafts can be set during operation. This results in a reduced compression at full load, but still can reach the limits of the load capacity of the engine.
Auf diese Weise kann der Motor sowohl im Teillast-Bereich als auch im Volllast-Bereich an den Grenzen seiner Belastbarkeit gefahren werden. Es kann somit, verglichen mit herkömmlichen Motoren, über den gesamten Lastbereich des Motors eine höhere Verdichtung erreicht werden. Bekanntlich ist die Ausnutzung der chemischen Energie des Kraftstoffs bei höherer Verdichtung besser. Somit kann mit der vorgeschlagenen Phasenverschiebung insgesamt eine höhere Ausnutzung der Energie des Brennstoffs und damit ein geringerer Brennstoff-Verbrauch erreicht werden.In this way, the engine can be driven both in the part-load range and in the full load range at the limits of its capacity. It can thus be achieved over the entire load range of the engine, a higher compression compared to conventional engines. As is known, the utilization of the chemical energy of the fuel is better with higher compression. Thus, with the proposed phase shift overall, a higher utilization of the energy of the fuel and thus a lower fuel consumption can be achieved.
Ein solcher Motor ist ohne Einschränkungen für die Serienfertigung geeignet, da weder extreme Komplexität vorliegt noch besonders enge Fertigungstoleranzen erforderlich sind, die bei anderen Motorkonstruktionen mit variabler Verdichtung für Probleme sorgen und beispielsweise zu hohe Fertigungskosten verursachen können.Such an engine is suitable for mass production without any restrictions, since neither extreme complexity nor particularly tight manufacturing tolerances are required, which cause problems in other engine designs with variable compression and can cause, for example, high manufacturing costs.
Alltagstauglich lässt sich eine solche Phasenverschiebung wie folgt realisieren:
- Jede Kurbelwelle trägt ein Synchronisationszahnrad, wobei die beiden Synchronisationszahnräder miteinander in Eingriff sind, um die beiden Kurbelwellen zu synchronisieren.
- Each crankshaft carries a synchronizing gear, the two synchronizing gears being engaged with each other to synchronize the two crankshafts.
Eine der beiden Kurbelwellen trägt ein Synchronisationszahnrad, welches um die Achse der Kurbelwelle rotieren kann. Ferner weist diese Kurbelwelle ein Verbindungselement auf, welches entlang der Achse der Kurbelwelle verschiebbar ist. Entsprechende Mittel zum Verschieben des Verbindungselements entlang der Achse der Kurbelwelle sind vorgesehen, die das Verbindungselement gegen das Synchronisationszahnrad pressen können.One of the two crankshafts carries a synchronization gear, which can rotate about the axis of the crankshaft. Furthermore, this crankshaft has a connecting element, which is displaceable along the axis of the crankshaft. Corresponding means for displacing the connecting element along the axis of the crankshaft are provided, which can press the connecting element against the synchronization gear.
Das Verbindungselement weist eine Rampe auf. Das Synchronisationszahnrad weist ebenfalls eine Rampe auf. Die Rampe des Verbindungselements und die Rampe des Synchronisationszahnrads sind derart angeordnet, dass sie formschlüssig aneinander angreifen.The connecting element has a ramp. The synchronization gear also has a ramp. The ramp of the connecting element and the ramp of the synchronization gear are arranged such that they engage positively with one another.
Mittels der Mittel zum Verschieben des Verbindungselements und der beiden Rampen kann die Winkelstellung des Synchronisationszahnrads auf der Kurbelwelle variiert werden.By means of the means for displacing the connecting element and the two ramps, the angular position of the synchronization gear on the crankshaft can be varied.
Eine andere, ebenfalls sehr robuste Art, die Phasenverschiebung der beiden Kurbelwellen gegeneinander zu realisieren, stellt sich wie folgt dar: Wiederum hat jede Kurbelwelle ein Synchronisationszahnrad trägt, wobei die beiden Synchronisationszahnräder miteinander in Eingriff sind, um die beiden Kurbelwellen zu synchronisieren. Eine der beiden Kurbelwellen trägt wiederum ein Synchronisationszahnrad, welches um die Achse der Kurbelwelle rotieren kann. Die Winkelstellung dieses Synchronisationszahnrads bezogen auf diese Kurbelwelle kann hydraulisch variiert werden.Another, also very robust way to realize the phase shift of the two crankshafts against each other, is as follows: Again, each crankshaft has a synchronizing gear, wherein the two synchronization gears are engaged with each other to synchronize the two crankshafts. One of the two crankshafts in turn carries a synchronization gear which can rotate about the axis of the crankshaft. The angular position of this synchronization gear relative to this crankshaft can be varied hydraulically.
Weitere Einzelheiten und Merkmale ergeben sich aus der nachfolgenden Beschreibung von bevorzugten Ausführungsbeispielen in Verbindung mit den Unteransprüchen. Hierbei können die jeweiligen Merkmale für sich alleine oder zu mehreren in Kombination miteinander verwirklicht sein. Die Möglichkeiten, die Aufgabe zu lösen, sind nicht auf die Ausführungsbeispiele beschränkt. So umfassen beispielsweise Bereichsangaben stets alle - nicht genannten - Zwischenwerte und alle denkbaren Teilintervalle.Further details and features will become apparent from the following description of preferred embodiments in conjunction with the subclaims. In this case, the respective features can be implemented on their own or in combination with one another. The possibilities to solve the problem are not limited to the embodiments. For example, area information always includes all - not mentioned - intermediate values and all imaginable subintervals.
Die Ausführungsbeispiele sind in den Figuren schematisch dargestellt. Gleiche Bezugsziffern in den einzelnen Figuren bezeichnen dabei gleiche oder funktionsgleiche bzw. hinsichtlich ihrer Funktionen einander entsprechende Elemente. Im Einzelnen zeigt:
- Fig. 1
- eine schematische Querschnittansicht durch einen Doppelkurbelwellenmotor, ohne Phasenverschiebung der Kurbelwellen gegeneinander;
- Fig. 2
- eine schematische Querschnittsansicht durch einen erfindungsgemäßen Doppelkurbelwellenmotor, wobei beide Kurbelwellen gegeneinander phasenverschoben sind;
- Fig. 3
- eine Darstellung der Kinematik des Doppelkurbelwellenmotors;
- Fig. 4
- eine Darstellung des zusätzlichen Kolbenhubs eines erfindungsgemäßen Motors in Abhängigkeit von der Phasenverschiebung der beiden Kurbelwellen gegeneinander;
- Fig.5
- eine Darstellung des Verdichtungsverhältnisses eines erfindungsgemäßen Motors in Abhängigkeit von der Phasenverschiebung der beiden Kurbelwellen gegeneinander;
- Fig. 6
- eine Darstellung des thermischen Wirkungsgrades eines erfindungsgemäßen Motors in Abhängigkeit von der Phasenverschiebung der beiden Kurbelwellen gegeneinander;
- Fig. 7
- eine schematische Ansicht einer bevorzugten Ausführungsform der Mittel zur Phasenverschiebung der Kurbelwellen; und
- Fig. 8
- eine schematische Ansicht einer weiteren Ausführungsform der Mittel zur Phasenverschiebung der Kurbelwellen.
- Fig. 1
- a schematic cross-sectional view through a double crankshaft motor, without phase shift of the crankshafts against each other;
- Fig. 2
- a schematic cross-sectional view through a double crankshaft motor according to the invention, wherein both crankshafts are out of phase with each other;
- Fig. 3
- a representation of the kinematics of the double crankshaft motor;
- Fig. 4
- a representation of the additional piston stroke of an engine according to the invention in dependence on the phase shift of the two crankshafts against each other;
- Figure 5
- a representation of the compression ratio of an engine according to the invention in dependence on the phase shift of the two crankshafts against each other;
- Fig. 6
- a representation of the thermal efficiency of an engine according to the invention in dependence on the phase shift of the two crankshafts against each other;
- Fig. 7
- a schematic view of a preferred embodiment of the means for phase shifting the crankshafts; and
- Fig. 8
- a schematic view of another embodiment of the means for phase shifting the crankshaft.
In dieser Figur sind die beiden Kurbelwellen nicht gegeneinander phasenverschoben. Der Verbrennungsraum 9, der im oberen Totpunkt oberhalb des Kolbens vorhanden ist, ist so klein wie möglich, daher die Verdichtung maximal. Bei einem erfindungsgemäßen Motor, der außerdem über Mittel zur Phasenverschiebung der beiden Kurbelwellen gegeneinander verfügt, liegt dieser Zustand zweckmäßigerweise beim Teillastbetrieb vor, für den der Motor optimiert sein kann.In this figure, the two crankshafts are not out of phase with each other. The
In
In
In
Entsprechende Mittel 80 zum Verschieben des Verbindungselements 70 entlang der Achse der Kurbelwelle 50 sind vorgesehen, die das Verbindungselement 70 gegen das Synchronisationszahnrad 60 pressen können und dieses somit fest an die Rotation der Kurbelwelle 50 koppeln. Diese Mittel 80 können z. B. ein hydraulischer oder elektrischer Versteller sein. In
Das Verbindungselement 70 weist dazu an seinem dem Synchronisationszahnrad 60 zugewandten Ende eine Rampe 90 auf. Das Synchronisationszahnrad 60 hat eine komplementär ausgestaltete Rampe 95. Die beiden Rampen 90, 95 sind derart angeordnet, dass sie formschlüssig aneinander angreifen können. Je nach Stellung des Verbindungselements 70 entlang der Achse der Kurbelwelle 50 wird das Synchronisationszahnrad 60 also in mehr oder weniger verdrehter Stellung an der Kurbelwelle 50 fixiert, wodurch gegenüber der anderen Kurbelwelle, deren Synchronisationszahnrad in herkömmlicher Weise fest mit ihr verbunden ist, eine Phasenverschiebung erzielt wird.The connecting
Eine weitere Ausführungsform der Mittel zur Phasenverschiebung der Kurbelwellen gegeneinander ist ein Flügelzellenversteller, wie in
Verbrennungsmotor mit zwei Kurbelwellen, wobei in jedem Zylinder ein Kolben angeordnet ist, der mittels zweier Pleuel jeweils auf beide Kurbelwellen wirkt.Internal combustion engine with two crankshafts, wherein in each cylinder a piston is arranged, which acts on both crankshafts by means of two connecting rods.
Ein Verbrennungsmotor ist eine Verbrennungskraftmaschine, die chemische Energie eines Kraftstoffs durch Verbrennung in mechanische Arbeit umwandelt. Die Verbrennung findet dabei im Brennraum statt, in dem ein Gemisch aus Kraftstoff und Umgebungsluft gezündet wird. Die Wärmeausdehnung des durch die Verbrennung heißen Gases wird genutzt, um einen Kolben zu bewegen. Geläufige Beispiele für Verbrennungsmotoren sind der Ottomotor und der Dieselmotor, z.B. in Automobilen.An internal combustion engine is an internal combustion engine that converts chemical energy of a fuel into mechanical work by combustion. The combustion takes place in the combustion chamber, in which a mixture of fuel and ambient air is ignited. The thermal expansion of the hot gas is used to move a piston. Common examples of internal combustion engines are the gasoline engine and the diesel engine, e.g. in automobiles.
Beim Doppelkurbelwellenmotor ist unter Phasenverschiebung folgendes zu verstehen: Die beiden Kurbelwellen laufen gleichphasig, wenn die zugehörigen Pleuel eines Zylinders jeweils gleichzeitig ihre höchste Position erreichen. Der Kolben befindet sich dann in seinem oberen Totpunkt. Erreichen die beiden Pleuel eines Zylinders ihre höchste Position zu unterschiedlichen Zeitpunkten, so hat das eine Pleuel noch einen Winkel (der positiv oder negativ sein kann) bis zu seiner höchsten Position zurückzulegen, wenn das andere sich gerade in seiner höchsten Position befindet. Dieser Winkel ist die Phasenverschiebung der beiden Kurbelwellen.The double crankshaft engine is to be understood as phase shifting: The two crankshafts run in phase when the associated connecting rods of a cylinder each reach their highest position at the same time. The piston is then in its top dead center. If the two connecting rods of a cylinder reach their highest position at different times, then one connecting rod still has to cover one angle (which may be positive or negative) up to its highest position, when the other is in its highest position. This angle is the phase shift of the two crankshafts.
Als Verdichtungsverhältnis bezeichnet man bei Verbrennungsmotoren das Verhältnis des gesamten Zylinderraumes vor der Verdichtung zum verbliebenen Raum nach der Verdichtung. Mit höherem Verdichtungsverhältnis steigt der Wirkungsgrad an, gleichzeitig nimmt bei Ottomotoren allerdings auch die Klopfneigung zu. Das Klopfen kann wiederum durch Benzin mit höherer Oktanzahl, Optimierung der Brennraumform oder den Einsatz mehrerer Zündkerzen reduziert werden. Als grober Anhaltswert für den Kraftstoffverbrauch gilt: eine Erhöhung des Verdichtungsverhältnisses um einen Punkt verringert den Verbrauch um etwa 2%. (Nach http://de.wikipedia.org/wiki/Verdichtungsverh%C3%A4ltnis)
-
DE 103 48 345 B4DE 103 48 345 B4 -
EP 2 426 336 A2 EP 2 426 336 A2 -
US 5,329,893US 5,329,893 -
US 2005/0028760 A1US 2005/0028760 A1 -
WO 01/23722 A1WO 01/23722 A1 -
DE 10 2004 051 012 A1 DE 10 2004 051 012 A1 -
WO 2007/081222 A1WO 2007/081222 A1 -
DE 103 09 651 A1DE 103 09 651 A1 -
DE 103 09 652 A1DE 103 09 652 A1 -
EP 1 247 958 A1 EP 1 247 958 A1 -
WO 2008/099018 A1WO 2008/099018 A1
Claims (3)
dadurch gekennzeichnet,
characterized,
dadurch gekennzeichnet,
characterized,
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13002068.8A EP2792846A1 (en) | 2013-04-19 | 2013-04-19 | Double crankshaft combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13002068.8A EP2792846A1 (en) | 2013-04-19 | 2013-04-19 | Double crankshaft combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2792846A1 true EP2792846A1 (en) | 2014-10-22 |
Family
ID=48182700
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13002068.8A Withdrawn EP2792846A1 (en) | 2013-04-19 | 2013-04-19 | Double crankshaft combustion engine |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP2792846A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017063751A1 (en) * | 2015-10-16 | 2017-04-20 | Peter Pelz | Internal combustion engine with double crank drive and variable compression ratio |
EP3163014A1 (en) * | 2015-10-21 | 2017-05-03 | Neander Motors AG | Pivot bearing for two connecting rods |
EP3171000A1 (en) * | 2015-11-17 | 2017-05-24 | Neander Motors AG | Engine with piston having two piston bolts |
US10047670B2 (en) | 2015-01-07 | 2018-08-14 | Neander Motors Ag | Internal combustion engine having at least one piston |
Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5058537A (en) * | 1989-04-21 | 1991-10-22 | Paul Marius A | Optimized high pressure internal combustion engines |
US5329893A (en) | 1990-12-03 | 1994-07-19 | Saab Automobile Aktiebolag | Combustion engine with variable compression ratio |
US5732673A (en) * | 1996-11-08 | 1998-03-31 | Mandella; Michael J. | Triple-crankshaft variable stroke engine |
WO2001023722A1 (en) | 1999-09-27 | 2001-04-05 | Edward Charles Mendler | Rigid crankshaft cradle and actuator |
DE10019959A1 (en) * | 2000-04-20 | 2001-10-25 | Gerhard Klaiber | Control method for IC engine uses variation in engine compression and alteration of crankshaft synchronization to change their relative positions |
EP1247958A1 (en) | 2001-04-07 | 2002-10-09 | Ford Global Technologies, Inc., A subsidiary of Ford Motor Company | Combuistion engine with variable compression ratio |
DE10309651A1 (en) | 2003-03-06 | 2004-09-23 | Daimlerchrysler Ag | Reciprocating piston IC engine e.g. for automobile, has eccentric used for adjusting piston stroke selectively locked relative to crankshaft pin by hydraulically-controlled locking element |
DE10309652A1 (en) | 2003-03-06 | 2004-09-23 | Daimlerchrysler Ag | Internal combustion engine for e.g. motor vehicle, has locking device used to securely latch to eccentric cam to prevent eccentric cam from rotating if desired |
US20050028760A1 (en) | 2003-08-08 | 2005-02-10 | Toyota Jidosha Kabushiki Kaisha | Variable compression ratio mechanism |
DE10348345B4 (en) | 2003-10-17 | 2005-09-01 | Neander-Motorfahrzeuge Gmbh | Reciprocating internal combustion engine |
DE102004051012A1 (en) | 2004-10-20 | 2006-04-27 | Daimlerchrysler Ag | Lifting cylinder internal combustion engine with variable compression has two mass flywheel with its primary winding connected to the crankshaft and secondary winding connected to transmission |
WO2007081222A1 (en) | 2006-01-16 | 2007-07-19 | Brian Barradine | Variable compression system for internal combustion engines |
DE102006060660A1 (en) * | 2006-12-21 | 2008-06-26 | Neander Motors Ag | Piston machine for operating as an engine, a pump or a compressor has a piston-cylinder unit with a cylinder having a piston moving to and fro in it and crankshafts |
WO2008099018A1 (en) | 2007-02-16 | 2008-08-21 | Gomecsys B.V. | A reciprocating piston mechanism, a method of assembling this, and an internal combustion engine |
US20100025138A1 (en) * | 2008-07-29 | 2010-02-04 | Ruscak Ian M | Centrifugal advance mechanism |
US20120042841A1 (en) * | 2010-08-19 | 2012-02-23 | Nippon Soken, Inc. | Valve timing control apparatus |
EP2426336A2 (en) | 2010-09-04 | 2012-03-07 | Neander Motors AG | Piston with two pivot bearings and double crankshaft piston engine |
-
2013
- 2013-04-19 EP EP13002068.8A patent/EP2792846A1/en not_active Withdrawn
Patent Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5058537A (en) * | 1989-04-21 | 1991-10-22 | Paul Marius A | Optimized high pressure internal combustion engines |
US5329893A (en) | 1990-12-03 | 1994-07-19 | Saab Automobile Aktiebolag | Combustion engine with variable compression ratio |
US5732673A (en) * | 1996-11-08 | 1998-03-31 | Mandella; Michael J. | Triple-crankshaft variable stroke engine |
WO2001023722A1 (en) | 1999-09-27 | 2001-04-05 | Edward Charles Mendler | Rigid crankshaft cradle and actuator |
DE10019959A1 (en) * | 2000-04-20 | 2001-10-25 | Gerhard Klaiber | Control method for IC engine uses variation in engine compression and alteration of crankshaft synchronization to change their relative positions |
EP1247958A1 (en) | 2001-04-07 | 2002-10-09 | Ford Global Technologies, Inc., A subsidiary of Ford Motor Company | Combuistion engine with variable compression ratio |
DE10309651A1 (en) | 2003-03-06 | 2004-09-23 | Daimlerchrysler Ag | Reciprocating piston IC engine e.g. for automobile, has eccentric used for adjusting piston stroke selectively locked relative to crankshaft pin by hydraulically-controlled locking element |
DE10309652A1 (en) | 2003-03-06 | 2004-09-23 | Daimlerchrysler Ag | Internal combustion engine for e.g. motor vehicle, has locking device used to securely latch to eccentric cam to prevent eccentric cam from rotating if desired |
US20050028760A1 (en) | 2003-08-08 | 2005-02-10 | Toyota Jidosha Kabushiki Kaisha | Variable compression ratio mechanism |
DE10348345B4 (en) | 2003-10-17 | 2005-09-01 | Neander-Motorfahrzeuge Gmbh | Reciprocating internal combustion engine |
DE102004051012A1 (en) | 2004-10-20 | 2006-04-27 | Daimlerchrysler Ag | Lifting cylinder internal combustion engine with variable compression has two mass flywheel with its primary winding connected to the crankshaft and secondary winding connected to transmission |
WO2007081222A1 (en) | 2006-01-16 | 2007-07-19 | Brian Barradine | Variable compression system for internal combustion engines |
DE102006060660A1 (en) * | 2006-12-21 | 2008-06-26 | Neander Motors Ag | Piston machine for operating as an engine, a pump or a compressor has a piston-cylinder unit with a cylinder having a piston moving to and fro in it and crankshafts |
WO2008099018A1 (en) | 2007-02-16 | 2008-08-21 | Gomecsys B.V. | A reciprocating piston mechanism, a method of assembling this, and an internal combustion engine |
US20100025138A1 (en) * | 2008-07-29 | 2010-02-04 | Ruscak Ian M | Centrifugal advance mechanism |
US20120042841A1 (en) * | 2010-08-19 | 2012-02-23 | Nippon Soken, Inc. | Valve timing control apparatus |
EP2426336A2 (en) | 2010-09-04 | 2012-03-07 | Neander Motors AG | Piston with two pivot bearings and double crankshaft piston engine |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10047670B2 (en) | 2015-01-07 | 2018-08-14 | Neander Motors Ag | Internal combustion engine having at least one piston |
WO2017063751A1 (en) * | 2015-10-16 | 2017-04-20 | Peter Pelz | Internal combustion engine with double crank drive and variable compression ratio |
EP3163014A1 (en) * | 2015-10-21 | 2017-05-03 | Neander Motors AG | Pivot bearing for two connecting rods |
US9869342B2 (en) | 2015-10-21 | 2018-01-16 | Neander Motors Ag | Pivot bearing for two connecting rods |
EP3171000A1 (en) * | 2015-11-17 | 2017-05-24 | Neander Motors AG | Engine with piston having two piston bolts |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102013225063A1 (en) | Connecting rod of an internal combustion engine with variable length | |
WO2001092700A1 (en) | Device for modifying the compression of a cylinder in an ic piston engine | |
DE102011018166A1 (en) | Device for changing a compression ratio of a reciprocating internal combustion engine | |
DE112017002489B4 (en) | Double crankshaft engine | |
EP3362645B1 (en) | Internal combustion engine with double crank drive and variable compression ratio | |
DE102014220177A1 (en) | Device for changing compression ratios | |
EP2792846A1 (en) | Double crankshaft combustion engine | |
DE102014217531A1 (en) | Valve lift control device with cylinder deactivation | |
DE102010061359A1 (en) | Switching valve for controlling fluid flow in combustion engine of vehicle, comprises switching unit, which is adapted to shift switching valve into primary switching position and secondary switching position | |
DE102012214659B4 (en) | Length-adjustable connecting rod and method of operating an internal combustion engine with such a connecting rod | |
DE102017207644A1 (en) | Method for changing a cylinder-related compression ratio e of a spark-ignited internal combustion engine and internal combustion engine for carrying out such a method | |
DE102008038076A1 (en) | Piston for reciprocating engine e.g. petrol engine, of motor vehicle, has piston pin bearing comprising eccentric element, where axis of piston pin is eccentrically adjustable by rotational adjustment of eccentric element | |
DE102016212064A1 (en) | Device for changing a compression ratio of a reciprocating internal combustion engine | |
DE102013019214B3 (en) | Multi-joint crank drive of an internal combustion engine and method for operating a multi-joint crank drive | |
DE102015223129A1 (en) | Hydraulically operated switching valve | |
DE102008038090A1 (en) | Control device for locking adjustable piston pin supported at piston of reciprocating-piston engine e.g. diesel engine, has operating element i.e. key element, that moves locking element indirectly between locking and releasing positions | |
DE102010009911B3 (en) | Internal combustion engine operating method, involves adjusting lever element between turning positions for adjusting compression ratios of internal combustion engine, and supporting adjusting device at crank case of engine | |
DE10352737B4 (en) | Internal combustion engine with a variable compression space | |
DE102015221908A1 (en) | Device for changing the compression ratio of a reciprocating internal combustion engine | |
DE102018210265B4 (en) | Pistons for an internal combustion engine and method for operating an internal combustion engine with such a piston | |
DE102014018898A1 (en) | Multi-joint crank drive for an internal combustion engine with an eccentric shaft actuator comprising a switchable transmission with at least two different reduction ratios | |
DE102011078648B4 (en) | Internal combustion engine with crank mechanism | |
DE9313192U1 (en) | The connecting rod engine | |
DE102014223597B4 (en) | Roller for a roller tappet of a high-pressure fuel pump, roller tappet, high-pressure fuel pump and internal combustion engine | |
DE10249187A1 (en) | Support device and method for a variable valve mechanism |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20130419 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20150423 |