DE3644721A1 - Device for a reciprocating piston engine with variable combustion chamber - Google Patents

Device for a reciprocating piston engine with variable combustion chamber

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Publication number
DE3644721A1
DE3644721A1 DE19863644721 DE3644721A DE3644721A1 DE 3644721 A1 DE3644721 A1 DE 3644721A1 DE 19863644721 DE19863644721 DE 19863644721 DE 3644721 A DE3644721 A DE 3644721A DE 3644721 A1 DE3644721 A1 DE 3644721A1
Authority
DE
Germany
Prior art keywords
crankshaft
eccentric
shaft
bearings
countershaft
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Withdrawn
Application number
DE19863644721
Other languages
German (de)
Inventor
Erich Schmid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to DE19863644721 priority Critical patent/DE3644721A1/en
Publication of DE3644721A1 publication Critical patent/DE3644721A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • F16H21/28—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric with cams or additional guides
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

The aim of this device is an optimum compression in all speed and load ranges. In order to achieve this, the crankshaft (1) Fig. 1, is supported in eccentric bearings (4) Fig. 1. By radial swivelling of the eccentric bearings (4), performed by a control unit and an actuating mechanism, the crankshaft (1) together with the positively connected connecting rods (5) and pistons (6) Fig. 1 is raised or lowered thereby making the geometry of the combustion chamber (9) Fig. 1 adjustable. The output of the crankshaft (1) is by way of a countershaft transmission. Since the crankshaft (1) has no axial-linear connection to the transmission input shaft due to the rising and falling movements or swivelling about the centre point (3) of the eccentric bearing (4), a countershaft transmission to the transmission input shaft is necessary for the output. In order to achieve this, the housing (16) is fixed to the last eccentric bearing (4) on the output side of the engine, the countershaft (17) being supported in the housing (16) and thereby rotating or swivelling about the centre point (3) of the eccentric bearing (4). The line of forces thereby runs from the gear (18) seated on the crankshaft (1) by way of the non-positively connected gears (19 and 20) supported on the countershaft (17) to the gear (21) on the shaft (15). <IMAGE>

Description

Die Erfindung betrifft eine Kurbelwellenanordnung gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a crankshaft arrangement according to the Preamble of claim 1.

Betrachtet man eine Hubkolbenmaschine, so ist das geometrische Verdichtungsverhältnis eine rein theoretische Größe, die praktisch nur im Vollastbetrieb erreicht wird, so daß das reale Verdichtungsverhältnis im Teillastbereich wesentlich niedriger liegt.If you look at a reciprocating piston machine, it is geometrical Compression ratio a purely theoretical quantity that is practically only achieved at full load, so that the real Compression ratio in the partial load range significantly lower lies.

Um die optimale Verdichtung in sämtlichen Drehzahl- und Last­ bereichen zu erreichen, wird bei dieser Erfindung die Kurbel­ welle (1) mit ihren Hauptlagern (2) Fig. 1, 2, 3 und 4 außerhalb des Mittelpunktes (3) Fig. 1 und 2 der Lager (4) gelagert, so daß bei einer geringen radialen Schwenkung der exzentrischen Lager (4) die Kurbelwelle (1) mit dem über die Pleuelstangen (5) Fig. 1, 2, 3 und 4 formschlüssig verbundenen Kolben (6) Fig. 1, 2 und 3 zu dem Zylinder (7) bzw. Zylinderkopf (8) Fig. 1, 2 und 3 gehoben oder gesenkt werden kann, wobei der Brennraum (9) Fig. 1, 2 und 3 bei gehobener Stellung kleiner ist als bei gesenkter Stellung.In order to achieve the optimal compression in all speed and load ranges, the crankshaft ( 1 ) with its main bearings ( 2 ) Fig. 1, 2, 3 and 4 outside the center ( 3 ) Figs. 1 and 2 in this invention the bearing ( 4 ) is mounted, so that with a slight radial pivoting of the eccentric bearing ( 4 ) the crankshaft ( 1 ) with the connecting rod ( 5 ) Fig. 1, 2, 3 and 4 positively connected piston ( 6 ) Fig. 1, 2 and 3 to the cylinder ( 7 ) or cylinder head ( 8 ) Fig. 1, 2 and 3 can be raised or lowered, the combustion chamber ( 9 ) Fig. 1, 2 and 3 is smaller than in the raised position lowered position.

Die Schwenkbewegung der exzentrischen Lager (4) wird über ein Steuergerät und eine Betätigungsmechanik auf die Lager (4) ausgeführt. Bei dieser Erfindung wird die Schwenkung der exzentrischen Lager (4) über die Welle (10) Fig. 1, 2 und 4 mit ihren Klauen (12) auf die Kulissensteine (14) und auf die Bolzen (13), welche in den Gabeln der exzentrischen Lager (4) angebracht sind, übertragen. The pivoting movement of the eccentric bearings (4) is performed via a control unit and an actuating mechanism to the bearing (4). In this invention, the pivoting of the eccentric bearing ( 4 ) on the shaft ( 10 ) Fig. 1, 2 and 4 with its claws ( 12 ) on the sliding blocks ( 14 ) and on the bolts ( 13 ), which in the forks of eccentric bearings ( 4 ) are attached, transferred.

Es ist anzumerken, daß die Betätigungsmechanik zur Schwenkung der exzentrischen Lager (4) auch mit anderen Konstruktionen gelöst werden kann, z.B. über eine Exzenterwelle oder einen hydraulischen Zylinder direkt usw.It should be noted that the actuating mechanism for pivoting the eccentric bearings ( 4 ) can also be solved with other constructions, for example directly via an eccentric shaft or a hydraulic cylinder, etc.

Die exzentrischen Lager (4) können auch mechanisch starr mit­ einander verbunden sein, was in den Zeichnungen nicht aufge­ führt ist.The eccentric bearing ( 4 ) can also be mechanically rigidly connected to one another, which is not shown in the drawings.

Die exzentrischen Lager (4) sind geteilt, um die Montage der Kurbelwelle (1) und ihrer Hauptlager (2) zu ermöglichen.The eccentric bearings ( 4 ) are split to allow the crankshaft ( 1 ) and its main bearings ( 2 ) to be assembled.

Der Abtrieb von der Kurbelwelle (1) erfolgt über ein Vorgelege­ getriebe. Da die Kurbelwelle (1) durch die Heb- und Senkbe­ wegungen bzw. die Schwenkung um den Mittelpunkt (3) der exzentrischen Lager (4) keine axial-lineare Verbindung zur Getriebeeingangswelle hat, ist für den Abtrieb ein Vorgelege­ getriebe zur Getriebeeingangswelle erforderlich. Um dies zu erreichen, ist das Gehäuse (16) Fig. 4 und 5 mit dem letzten exzentrischen Lager (4) an der Abtriebseite des Motors fest verbunden, wobei die Vorgelegewelle (17) Fig. 4 und 5 in dem Gehäuse (16) gelagert ist und sich somit um den Mittelpunkt (3) der exzentrischen Lager (4) dreht bzw. schwenkt. Der Kraftfluß verläuft hiermit von dem auf der Kurbelwelle (1) sitzenden Zahnrad (18) Fig. 3, 4 und 5 über die auf der Vorgelegewelle (17) gelagerten und kraftschlüssig verbundenen Zahnräder (19) und (20) Fig. 4 und 5 zu dem Zahnrad (21) auf der Welle (15) Fig. 4 und 5, welche z.B. die Getriebeeingangswelle sein kann.The crankshaft ( 1 ) is driven by a countershaft gear. Since the crankshaft ( 1 ) by the lifting and lowering movements or the pivoting around the center ( 3 ) of the eccentric bearing ( 4 ) has no axially linear connection to the transmission input shaft, a countershaft transmission to the transmission input shaft is required for the output. To achieve this, the housing ( 16 ) Fig. 4 and 5 is firmly connected to the last eccentric bearing ( 4 ) on the output side of the motor, the countershaft ( 17 ) Fig. 4 and 5 mounted in the housing ( 16 ) is and thus rotates or pivots about the center point ( 3 ) of the eccentric bearing ( 4 ). The flow of force hereby runs from the gearwheel ( 18 ) FIGS. 3, 4 and 5 seated on the crankshaft ( 1 ) via the gearwheels ( 19 ) and ( 20 ) connected to the countershaft ( 17 ) and positively connected to FIGS. 4 and 5 the gear ( 21 ) on the shaft ( 15 ) Fig. 4 and 5, which can be, for example, the transmission input shaft.

Der Antrieb von der Kurbelwelle (1) für die Nockenwelle kann z.B. über Steuerkette oder Zahnriemen erfolgen, wobei zur Straffung der Steuerkette bzw. des Steuerzahnriemens Spannräder bzw. Spann­ rollen einwirken. Diese Lösung kann man auch für den Antrieb mit Keilriemen für die Nebenaggregate geltend machen.The drive from the crankshaft ( 1 ) for the camshaft can take place, for example, via a timing chain or toothed belt, tensioning wheels or tensioning rollers acting to tighten the timing chain or timing belt. This solution can also be used for the drive with V-belts for the auxiliary units.

Claims (8)

1. Vorrichtung für eine Hubkolbenmaschine, bei der während des Betriebes der Brennraum (9) Fig. 1, 2 und 3 in seiner Größe veränderlich ist.1. Device for a reciprocating piston machine, in which the size of the combustion chamber ( 9 ) FIGS. 1, 2 and 3 is variable during operation. 2. Vorrichtung nach dem Anspruch 1, dadurch gekennzeichnet, daß die Kurbelwelle (1) Fig. 1, 2, 3, 4 und 5 mit ihren Haupt­ lagern (2) Fig. 1, 2, 3 und 4 außerhalb des Mittelpunktes (3) Fig. 1 und 2 der exzentrischen Lager (4) Fig. 1, 2, 3, 4 und 5 gelagert ist.2. Device according to claim 1, characterized in that the crankshaft ( 1 ) Fig. 1, 2, 3, 4 and 5 with their main bearings ( 2 ) Fig. 1, 2, 3 and 4 outside the center ( 3 ) Fig. 1 and 2 of the eccentric bearings (4) Fig. 1, 2, 3, 4 and 5 is mounted. 3. Vorrichtung nach den Ansprüchen 1 und 2 dadurch gekennzeichnet, daß durch eine radiale Schwenkung der oxzentrischen Lager (4) die Kurbelwelle (1) mit dem über die Pleuelstange (5) Fig. 1, 2, 3 und 4 formschlüssig verbundenen Kolben (6) Fig. 1, 2 und 3 zu dem Zylinder (7) und Zylinderkopf (8) Fig. 1, 2 und 3 gehoben oder gesenkt werden kann. Dadurch wird bei der ange­ hobenen Stellung Fig. 1 der Brennraum (9) Fig. 1, 2 und 3 verkleinert und bei der gesenkten Stellung Fig. 2 und 3 der Kurbelwelle (1) der Brennraum (9) vergrößert.3. Device according to claims 1 and 2, characterized in that by a radial pivoting of the eccentric bearing ( 4 ) the crankshaft ( 1 ) with the connecting rod ( 5 ) Fig. 1, 2, 3 and 4 positively connected piston ( 6th ) Fig. 1, 2 and 3 to the cylinder ( 7 ) and cylinder head ( 8 ) Fig. 1, 2 and 3 can be raised or lowered. Thereby, the combustion chamber 1, 2 and 3 of the crankshaft (1) is in the attached position levied Fig. (9) Fig. 1 2 and 3 and reduced at the lowered position shown in Fig., The combustion chamber (9) increases. 4. Vorrichtung nach den Ansprüchen 1, 2 und 3 dadurch gekenn­ zeichnet, daß die exzentrischen Lager (4) geteilt sind, um die Montage der Kurbelwelle (1) und ihrer Hauptlager (2) zu ermöglichen. Die geteilten exzentrischen Lager (4) sind durch Schrauben (10) Fig. 1 zusammengehalten und in den Lagern (11) Fig. 1, 2, 3 und 4 gelagert.4. Device according to claims 1, 2 and 3 characterized in that the eccentric bearings ( 4 ) are divided to enable the assembly of the crankshaft ( 1 ) and its main bearing ( 2 ). The divided eccentric bearings ( 4 ) are held together by screws ( 10 ) Fig. 1 and stored in the bearings ( 11 ) Fig. 1, 2, 3 and 4. 5. Vorrichtung nach den Ansprüchen 1, 2, 3 und 4 dadurch gekenn­ zeichnet, daß die exzentrischen Lager (4) über die Klauen (12) Kulissensteine (14) und Bolzen (13) Fig. 1, 2 und 4 kraft­ schlüssig mit der Welle (10) Fig. 1, 2 und 4 gekoppelt sind, somit werden die Bewegungen der Welle (10), welche z.B. von einem Stellmotor oder einem elektro-hydraulischen Stellglied ausgeführt werden, von der Welle (10) auf die exzentrischen Lager (4) übertragen. 5. Device according to claims 1, 2, 3 and 4 characterized in that the eccentric bearing ( 4 ) on the claws ( 12 ) sliding blocks ( 14 ) and bolts ( 13 ) Fig. 1, 2 and 4 forcefully with the Shaft ( 10 ) Fig. 1, 2 and 4 are coupled, so the movements of the shaft ( 10 ), which are carried out, for example, by a servomotor or an electro-hydraulic actuator, from the shaft ( 10 ) to the eccentric bearing ( 4th ) transfer. 6. Vorrichtung nach den Ansprüchen 1, 2, 3, 4 und 5 dadurch gekennzeichnet, daß der Abtrieb von der Kurbelwelle (1), welcher sich um den Mittelpunkt (3) schwenkt, zu der Welle (15) Fig. 4 und 5 über ein Vorgelege erfolgt.6. Device according to claims 1, 2, 3, 4 and 5, characterized in that the output from the crankshaft ( 1 ), which pivots about the center point ( 3 ), to the shaft ( 15 ) Figs. 4 and 5 there is a reduction gear. 7. Vorrichtung nach den Ansprüchen 1, 2, 3, 4, 5 und 6 dadurch gekennzeichnet, daß das Gehäuse (16) Fig. 4 und 5 mit dem letzten exzentrischen Lager (4) fest verbunden ist, wobei die Vorgelegewelle (17) Fig. 4 und 5, welche in dem Gehäuse (16) gelagert ist, sich um den Mittelpunkt (3) des exzentrischen Lagers (4) schwenkt, somit verläuft der Kraftfluß von dem auf der Kurbelwelle (1) sitzenden Zahn­ rad (18) Fig. 3, 4 und 5 über die auf der Vorgelegewelle (17) gelagerten und kraftschlüssig verbundenen Zahnräder (19 und 20) Fig. 4 und 5 zu dem Zahnrad (21) Fig. 4 und 5 auf der Welle (15). Von der Welle (15) kann der Abtrieb zum Getriebe erfolgen.7. Device according to claims 1, 2, 3, 4, 5 and 6 characterized in that the housing ( 16 ) Fig. 4 and 5 with the last eccentric bearing ( 4 ) is fixedly connected, the countershaft ( 17 ) Fig ., which is 4, and 5 mounted in the housing (16) pivots around the center (3) of the eccentric bearing (4), thus the power flow runs from the seated on the crankshaft (1) gear wheel (18) Fig. 3, 4 and 5 on the countershaft ( 17 ) mounted and non-positively connected gears ( 19 and 20 ) Fig. 4 and 5 to the gear ( 21 ) Fig. 4 and 5 on the shaft ( 15 ). From the shaft ( 15 ) the output can take place to the gearbox. 8. Vorrichtung nach den Ansprüchen 1, 2, 3, 4, 5, 6 und 7 dadurch gekennzeichnet, daß die exzentrischen Lager (4) mechanisch starr miteinander verbunden sind, was in den Zeichnungen nicht aufgeführt ist.8. Device according to claims 1, 2, 3, 4, 5, 6 and 7 characterized in that the eccentric bearings ( 4 ) are mechanically rigidly connected to one another, which is not shown in the drawings.
DE19863644721 1986-12-30 1986-12-30 Device for a reciprocating piston engine with variable combustion chamber Withdrawn DE3644721A1 (en)

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Application Number Priority Date Filing Date Title
DE19863644721 DE3644721A1 (en) 1986-12-30 1986-12-30 Device for a reciprocating piston engine with variable combustion chamber

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DE19863644721 DE3644721A1 (en) 1986-12-30 1986-12-30 Device for a reciprocating piston engine with variable combustion chamber

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4028594A1 (en) * 1990-09-08 1992-03-12 Hella Kg Hueck & Co Compression ratio setter for IC engine - calculates desired value of ratiofrom smoothed readings from detectors of engine and fuel parameters
WO1994000679A1 (en) * 1992-06-30 1994-01-06 Fanja Ltd A method for controlling the working cycle in an internal combustion engine and an engine for performing said method
WO1994000681A1 (en) * 1992-06-30 1994-01-06 Fanja Ltd. A method and a device for changing the compression ratio in an internal combustion engine
DE4226361A1 (en) * 1992-08-10 1994-04-07 Alex Zimmer Fuel-air mixt. compressing IC engine - has remaining space during compression varied w.r.t. mixt. feed quality in direction of best compression ratio
DE19757871A1 (en) * 1997-12-24 1999-07-01 Dieter Dipl Ing Reitz Internal combustion engine with changeable piston function
WO1999061766A1 (en) 1998-05-29 1999-12-02 Edward Charles Mendler Rigid crankshaft cradle and actuator
WO2000057074A1 (en) 1999-03-24 2000-09-28 Fev Motorentechnik Gmbh Coupling element for connecting two shafts which are parallel to an axis and arranged behind each other on the same axis with a cross-distance therebetween
WO2000057073A1 (en) 1999-03-24 2000-09-28 Fev Motorentechnik Gmbh Coupling element for connecting two shafts which are parallel to an axis and arranged behind each other on the same axis with a cross-distance therebetween
WO2000077368A1 (en) 1999-06-09 2000-12-21 Fev Motorentechnik Gmbh Piston-type internal combustion engine having a variable combustion chamber
US6247430B1 (en) 1997-10-31 2001-06-19 Fev Motorentechnik Gmbh & Co. Kommandgesellschaft Compression ratio setting device for an internal-combustion engine
US6260532B1 (en) 1998-09-28 2001-07-17 Edward Charles Mendler Rigid crankshaft cradle and actuator
EP1199452A1 (en) 2000-10-16 2002-04-24 FEV Motorentechnik GmbH Internal combustion engine with variable compression ratio and integrated setting actuator
EP1228298A1 (en) * 1999-11-12 2002-08-07 Edward Charles Mendler Rigid crankshaft cradle and actuator
US6443107B1 (en) 1999-05-27 2002-09-03 Edward Charles Mendler Rigid crankshaft cradle and actuator
WO2005098281A1 (en) 2004-03-31 2005-10-20 Edward Charles Mendler Chain drive
DE102005020270A1 (en) * 2005-04-30 2006-11-09 Daimlerchrysler Ag Internal combustion engine with variable compression ratio
WO2007123435A1 (en) * 2006-10-26 2007-11-01 Sergey Nikolaevich Afanasyev Internal combustion engine with variable compression rate
WO2007133109A1 (en) * 2006-12-01 2007-11-22 Sergey Nikolaevich Afanasyev Variable compression internal combustion engine
CN100351532C (en) * 2004-07-07 2007-11-28 张喜德 Transient reducing internal combustion engine crank shaft assembly
DE10008425B4 (en) * 1999-03-24 2007-12-20 Fev Motorentechnik Gmbh Coupling element for connecting two equiaxially one behind the other and with transverse distance from one another arranged axially parallel shafts, in particular for use on a reciprocating internal combustion engine with adjustable displacement of the crankshaft
CN100432374C (en) * 2003-01-02 2008-11-12 斯卡尔佐汽车研究股份有限公司 Mechanism for internal combustion piston engines
DE102008046426A1 (en) 2008-09-09 2010-03-11 Schaeffler Kg Compression ratio changing arrangement for combustion engine i.e. Otto engine, has spring unit partially absorbing gas and mass forces acting at positioning device during operation of engine in relation to actuating device
DE102008050826A1 (en) 2008-10-08 2010-04-15 Schaeffler Kg Adjusting device for changing position of crankshaft to adjust variable compression ratio of petrol engine, has rotation drive with lever coupled with adjusting shaft, where drive is designed as motor with actuator and reduction stage
DE102008050827A1 (en) 2008-10-08 2010-04-15 Schaeffler Kg Adjusting device for adjusting compression ratios of Otto engine crankshaft, has actuator displacing locking mechanism into free running position in fail-safe position to allow crankshaft to automatically take minimum compression position
DE19841381B4 (en) * 1997-10-31 2012-02-16 Fev Motorentechnik Gmbh Piston engine with adjustable compression ratio
DE202011002172U1 (en) 2011-02-01 2012-05-03 Kurt Imren Yapici pin coupling
DE102012019333A1 (en) * 2012-10-02 2014-04-03 Fev Gmbh Lubricant return device for a parallel crank gear of a reciprocating engine with an adjustable variable compression ratio
US8851030B2 (en) 2012-03-23 2014-10-07 Michael von Mayenburg Combustion engine with stepwise variable compression ratio (SVCR)
DE102013015467A1 (en) 2013-09-18 2015-03-19 Kurt Imren Yapici VCR compensation
DE112007000837B4 (en) 2006-04-11 2022-12-01 Eccing Expertenteams Gmbh I.G. Reciprocating engine with shiftable crankshaft

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4028594A1 (en) * 1990-09-08 1992-03-12 Hella Kg Hueck & Co Compression ratio setter for IC engine - calculates desired value of ratiofrom smoothed readings from detectors of engine and fuel parameters
WO1994000679A1 (en) * 1992-06-30 1994-01-06 Fanja Ltd A method for controlling the working cycle in an internal combustion engine and an engine for performing said method
WO1994000681A1 (en) * 1992-06-30 1994-01-06 Fanja Ltd. A method and a device for changing the compression ratio in an internal combustion engine
US5572959A (en) * 1992-06-30 1996-11-12 Fanja Ltd. Method for controlling the working cycle in an internal combustion engine and an engine for performing said method
US5605120A (en) * 1992-06-30 1997-02-25 Fanja Ltd. Method and a device for changing the compression ratio in an internal combustion engine
AU680419B2 (en) * 1992-06-30 1997-07-31 Fanja Ltd A method and a device for changing the compression ratio in an internal combustion engine
DE4226361A1 (en) * 1992-08-10 1994-04-07 Alex Zimmer Fuel-air mixt. compressing IC engine - has remaining space during compression varied w.r.t. mixt. feed quality in direction of best compression ratio
US6247430B1 (en) 1997-10-31 2001-06-19 Fev Motorentechnik Gmbh & Co. Kommandgesellschaft Compression ratio setting device for an internal-combustion engine
DE19841381B4 (en) * 1997-10-31 2012-02-16 Fev Motorentechnik Gmbh Piston engine with adjustable compression ratio
DE19757871A1 (en) * 1997-12-24 1999-07-01 Dieter Dipl Ing Reitz Internal combustion engine with changeable piston function
WO1999061766A1 (en) 1998-05-29 1999-12-02 Edward Charles Mendler Rigid crankshaft cradle and actuator
US6260532B1 (en) 1998-09-28 2001-07-17 Edward Charles Mendler Rigid crankshaft cradle and actuator
WO2000057074A1 (en) 1999-03-24 2000-09-28 Fev Motorentechnik Gmbh Coupling element for connecting two shafts which are parallel to an axis and arranged behind each other on the same axis with a cross-distance therebetween
WO2000057073A1 (en) 1999-03-24 2000-09-28 Fev Motorentechnik Gmbh Coupling element for connecting two shafts which are parallel to an axis and arranged behind each other on the same axis with a cross-distance therebetween
JP4741733B2 (en) * 1999-03-24 2011-08-10 エフ・エー・フアウ・モトーレンテヒニック・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング Coupling element for connecting two shafts arranged back and forth coaxially and axially parallel to each other and spaced laterally
JP2002540355A (en) * 1999-03-24 2002-11-26 エフ・エー・フアウ・モトーレンテヒニック・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング Coupling element for coupling two axis-parallel axes which are arranged coaxially back and forth and axially parallel to one another and laterally spaced apart
DE10008425B4 (en) * 1999-03-24 2007-12-20 Fev Motorentechnik Gmbh Coupling element for connecting two equiaxially one behind the other and with transverse distance from one another arranged axially parallel shafts, in particular for use on a reciprocating internal combustion engine with adjustable displacement of the crankshaft
US6443107B1 (en) 1999-05-27 2002-09-03 Edward Charles Mendler Rigid crankshaft cradle and actuator
WO2000077368A1 (en) 1999-06-09 2000-12-21 Fev Motorentechnik Gmbh Piston-type internal combustion engine having a variable combustion chamber
EP1228298A4 (en) * 1999-11-12 2004-03-24 Edward Charles Mendler Rigid crankshaft cradle and actuator
US6637384B1 (en) 1999-11-12 2003-10-28 Edward Charles Mendler Rigid crankshaft cradle and actuator
EP1228298A1 (en) * 1999-11-12 2002-08-07 Edward Charles Mendler Rigid crankshaft cradle and actuator
EP1199452A1 (en) 2000-10-16 2002-04-24 FEV Motorentechnik GmbH Internal combustion engine with variable compression ratio and integrated setting actuator
US6588384B2 (en) 2000-10-16 2003-07-08 Fev Motorentechnik Gmbh Apparatus for varying the compression ratio of an internal-combustion engine
DE10051271B4 (en) * 2000-10-16 2015-07-16 Fev Gmbh In their compression ratio adjustable piston internal combustion engine with integrated Verstellaktuator
CN100432374C (en) * 2003-01-02 2008-11-12 斯卡尔佐汽车研究股份有限公司 Mechanism for internal combustion piston engines
WO2005098281A1 (en) 2004-03-31 2005-10-20 Edward Charles Mendler Chain drive
CN100351532C (en) * 2004-07-07 2007-11-28 张喜德 Transient reducing internal combustion engine crank shaft assembly
DE102005020270A1 (en) * 2005-04-30 2006-11-09 Daimlerchrysler Ag Internal combustion engine with variable compression ratio
US7798109B2 (en) 2005-04-30 2010-09-21 Daimler Ag Internal combustion engine with a variable compression ratio
DE112007000837B4 (en) 2006-04-11 2022-12-01 Eccing Expertenteams Gmbh I.G. Reciprocating engine with shiftable crankshaft
WO2007123435A1 (en) * 2006-10-26 2007-11-01 Sergey Nikolaevich Afanasyev Internal combustion engine with variable compression rate
WO2007133109A1 (en) * 2006-12-01 2007-11-22 Sergey Nikolaevich Afanasyev Variable compression internal combustion engine
DE102008046426A1 (en) 2008-09-09 2010-03-11 Schaeffler Kg Compression ratio changing arrangement for combustion engine i.e. Otto engine, has spring unit partially absorbing gas and mass forces acting at positioning device during operation of engine in relation to actuating device
DE102008050827A1 (en) 2008-10-08 2010-04-15 Schaeffler Kg Adjusting device for adjusting compression ratios of Otto engine crankshaft, has actuator displacing locking mechanism into free running position in fail-safe position to allow crankshaft to automatically take minimum compression position
DE102008050826A1 (en) 2008-10-08 2010-04-15 Schaeffler Kg Adjusting device for changing position of crankshaft to adjust variable compression ratio of petrol engine, has rotation drive with lever coupled with adjusting shaft, where drive is designed as motor with actuator and reduction stage
DE202011002172U1 (en) 2011-02-01 2012-05-03 Kurt Imren Yapici pin coupling
US8851030B2 (en) 2012-03-23 2014-10-07 Michael von Mayenburg Combustion engine with stepwise variable compression ratio (SVCR)
DE102012019333A1 (en) * 2012-10-02 2014-04-03 Fev Gmbh Lubricant return device for a parallel crank gear of a reciprocating engine with an adjustable variable compression ratio
DE102013015467A1 (en) 2013-09-18 2015-03-19 Kurt Imren Yapici VCR compensation

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