WO2010108582A1 - Dispositif destiné à faire varier le rapport de compression dans un moteur à combustion interne - Google Patents

Dispositif destiné à faire varier le rapport de compression dans un moteur à combustion interne Download PDF

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Publication number
WO2010108582A1
WO2010108582A1 PCT/EP2010/001191 EP2010001191W WO2010108582A1 WO 2010108582 A1 WO2010108582 A1 WO 2010108582A1 EP 2010001191 W EP2010001191 W EP 2010001191W WO 2010108582 A1 WO2010108582 A1 WO 2010108582A1
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WO
WIPO (PCT)
Prior art keywords
connecting rod
piston pin
eccentric
upper connecting
piston
Prior art date
Application number
PCT/EP2010/001191
Other languages
German (de)
English (en)
Inventor
Willi Parsch
Original Assignee
Ixetic Bad Homburg Gmbh
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 Ixetic Bad Homburg Gmbh filed Critical Ixetic Bad Homburg Gmbh
Priority to DE112010001349T priority Critical patent/DE112010001349A5/de
Publication of WO2010108582A1 publication Critical patent/WO2010108582A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

Definitions

  • the invention relates to a device for changing the compression ratio in an internal combustion engine according to the preamble of claim 1.
  • Known devices serve to be able to realize different compression ratios in an internal combustion engine depending on the power requirement in order to at least temporarily increase the efficiency of the engine.
  • a lower compression ratio can be realized at full load to avoid knocking combustion.
  • the compression ratio can be increased, resulting in a considerable increase in the efficiency results.
  • Known devices comprise a connecting rod, which is articulated to a crankshaft with a lower connecting rod eye and to a piston with an upper connecting rod eye.
  • a piston pin is pivotally mounted in the piston. It is mounted eccentrically in the upper connecting rod eye and along a circular path around the center axis verlar ger.
  • a connecting rod length can be varied, which is measured from a central axis of the lower connecting rod to a central axis of the piston pin.
  • an actuating device is provided for the displacement of the piston pin.
  • this comprises articulation rods, via which a torque applied to the piston pin is supported on hydraulic pistons.
  • the connecting rods and hydraulic pistons are in the area of the connecting rod between the upper and provided the lower connecting rod and lead here to an effective broadening of the connecting rod.
  • the connecting rod is therefore on the one hand unwieldy and has an unfavorable shape, on the other hand, it includes a lot of additional moving masses that must be accelerated during the working cycle of the piston.
  • the object of the invention is therefore to provide a device which does not have the disadvantages mentioned and in particular comprises a compact connecting rod, in which the masses to be accelerated are significantly reduced.
  • a device having the features of claim 1. This is characterized in that the actuating device is arranged in the upper connecting rod eye.
  • the term "in the upper connecting rod eye” does not exclusively refer to the fact that the actuating device is preferably integrated in the clear opening of the upper connecting rod eye
  • the term "connecting rod eye” here refers to the part of the connecting rod in which the piston pin is mounted. Characterized in that the actuator is displaced from the region of the central rod in the upper connecting rod, the connecting rod may be similar or just as compact as a conventional connecting rod.
  • the Anlenkstangen and hydraulic pistons so that it has a reduced moving mass, which in turn power losses of the engine can be reduced due to the inertial forces to be overcome.
  • the actuating device comprises an eccentric, which carries the piston pin and is pivotally mounted in the upper connecting rod eye.
  • a device also comprises an actuating element, which can cause a pivoting of the eccentric about the central axis of the upper connecting rod.
  • the piston pin is thus arranged eccentrically on the eccentric, and a pivoting of the eccentric about the central axis of the upper connecting rod causes a displacement of the piston pin along a circular path about this axis.
  • a device which is characterized in that the actuating element is designed as a swivel motor.
  • the actuating element is designed as a swivel motor.
  • a device in which the actuating element has a rotor is also preferred.
  • a device which is characterized in that the piston pin is mounted in the eccentric.
  • the piston pin and eccentric are separate parts, which may be advantageous for manufacturing reasons.
  • the piston pin is formed integrally with the eccentric.
  • the work step in which otherwise the piston pin must be connected to the eccentric, is omitted.
  • the rotor of the actuating element has a substantially triangular-shaped recess, into which a likewise substantially triangular part of the eccentric engages, viewed in cross-section.
  • the eccentric is rotatably mounted in the rotor. Due to the complementary design of the recess of the rotor and the subsection of the eccentric in a simple geometric shape, a secure, non-rotatable mounting of the eccentric can be ensured in the rotor without major manufacturing effort. Due to the triangular shape, it is also possible to transmit large torques.
  • a device is preferred in which the rotor and the eccentric are rotatably connected to each other by a toothing.
  • a toothing Depending on the design of the toothing, an even greater torque can be transmitted than is the case with a triangular design of the recess in the rotor or the subsection of the eccentric which engages in the recess.
  • a device which is characterized in that the actuating device is hydraulically activated and / or fixable.
  • the activation of the actuator is responsive to this being put into a state in which a displacement of the piston pin can take place.
  • the fixation of the actuator speaks to a state in which no displacement of the piston pin can take place. It is advantageous to Hydraulic device to activate and / or fix, because in an internal combustion engine without further engine oil pressure is available for this purpose.
  • a device is also preferred in which the actuating device can be driven hydraulically.
  • the drive of the device indicates that it is not only released or locked due to the hydraulic pressure, but that the displacement of the piston pin by the actuator is actively effected by the hydraulic oil pressure.
  • the actuating device can be driven by mass and / or gas forces.
  • the actuating device can be hydraulically activated and / or fixed, for example, wherein in the activated state, a displacement of the piston pin is effected by acting in the course of a working game of the engine mass and / or gas forces. In the fixed state, these forces are at least partially absorbed by the hydraulic oil, if it is a hydraulically activated and / or fixable actuator, so they can not cause displacement of the piston pin.
  • a device is preferred in which a valve for hydraulic activation, fixation and / or to drive the actuator is provided.
  • the actuator is very easy to control, without this complicated mechanisms should be provided.
  • Figure 1 is a sectional view of the device of a first
  • Figure 2 is a sectional view of the device seen from a second viewing direction, perpendicular to the first
  • FIG. 1 shows a first sectional view of a device 1.
  • This comprises a connecting rod 3, which is articulated to a piston 7 with an upper connecting rod eye 5.
  • the connecting rod 3 also has a lower connecting rod eye 9, with which it is articulated on a crank pin 11 of a crankshaft.
  • the upper connecting rod 5 and the lower connecting rod 9 are connected by a central rod 13 of the connecting rod 3.
  • the device 1 further comprises a piston pin 15, which is pivotally mounted in the piston 7. It causes a mechanical coupling between the connecting rod 3 and the piston 7, so that it follows the movement of the connecting rod 3.
  • a longitudinal axis L1 of the connecting rod 3 is shown in dashed lines, which is arranged vertically. It is perpendicular to two horizontally arranged axes, which are indicated by dash-dotted lines, wherein the first marks a diameter line D1 of the upper connecting rod 5, and the second a diameter line D2 of the lower connecting rod eye 9.
  • the longitudinal axis LI and the diameter line D1 are therefore perpendicular to each other and intersect in the center of the upper connecting rod 5.
  • the longitudinal axis L1 and the Diameter line D2 perpendicular to each other and intersect in the center of the lower connecting rod eye.
  • a dotted line D3 of the piston pin 15 is shown in phantom, which is perpendicular to a second diameter line D4 of the piston pin 15 and this intersects in the center of the piston pin 15.
  • the diameter line D4 is also shown in phantom and runs parallel to the diameter line D1 of the upper connecting rod 5.
  • the piston pin 15 is mounted eccentrically in the upper connecting rod eye, which results from the fact that the intersection of its diameter lines D3, D4 does not coincide with the intersection of the axis L1 with the line D1. It is displaceable along a circular path about a central axis A of the upper connecting rod eye, which is perpendicular to the image plane and extends through the intersection of the axis L1 with the diameter line D1.
  • a displacement of the piston pin 15 along the mentioned circular path causes a change in a connecting rod length, which is determined either by the distance of the diameter lines D2 and D4, or alternatively by a central axis of the lower Pleu- leauges, which is perpendicular to the image plane and through the intersection of the Axis L1 with the diameter line D2 extends, to a central axis of the piston pin, which is also perpendicular to the image plane and passes through the intersection of the diameter lines D3, D4, can be measured.
  • the piston pin 15 is in an upper position in which the connecting rod length is maximum.
  • the top dead center of the piston 7 is a maximum upward - that is to one Cylinder head of the internal combustion engine 2, not shown, is displaced, resulting in a high compression ratio.
  • the diameter line D4 is arranged above the diameter line D1.
  • the piston pin 15 When the piston pin 15 is displaced along the mentioned circular path, it finally reaches a lower position, in which the diameter line D4 is arranged below the diameter line D1, wherein it preferably has the same distance to it as in FIG. 1.
  • the upper and the lower position of the piston pin 15 are preferably arranged symmetrically to the diameter line D1.
  • the connecting rod length is minimal, so that the top dead center of the piston 7 is also at a maximum distance from the cylinder head of the internal combustion engine. In this way, a small compression ratio is realized.
  • an actuating device 17 is provided for displacement of the piston pin 15.
  • This is arranged in the upper connecting rod 5.
  • the connecting rod 3 is thus composed of a total of three elements, namely the upper connecting rod 5, the central rod 13 and the lower connecting rod 9.
  • the actuating device 17 forms the upper connecting rod 5 as a first connecting rod element, wherein they a second connecting rod element comprising the lower connecting rod eye 9 and the middle rod 13 is connected to the formulation that the actuating device 17 is arranged in the upper connecting rod eye 5.
  • the actuating device 17 within a clear recess of the upper Pleuelauges 5 is arranged, such as the crank pin 11 in the lower connecting rod eye.
  • the actuating device 17 comprises an eccentric 19 and an actuating element 21.
  • the eccentric is mounted pivotably about the central axis A in the upper connecting rod eye 5.
  • the actuating element 21 is formed in the illustrated embodiment as a pivot motor.
  • actuating element 21 it is also possible to form the actuating element 21 as an electric motor. This is advantageous because no supply and discharge lines for Hydraulikö! must be provided.
  • a hydraulic swing motor is advantageous as actuator 21, because hydraulic oil in the form of engine oil is readily available in an internal combustion engine.
  • the swivel motor of the embodiment shown in Figure 1 has a rotor 23 and a housing 25.
  • the rotor has at least one wing, in this case three wings 27, 27 ', 27 ", which together with at least one projection, here three projections 29, 29', 29" of the housing 25 define at least two, here six pressure chambers in which only three pressure chambers 31, 31 ', 31 "can be seen in Figure 1, because the wings 27, 27', 27" at the projections 29, 29 ', 29 "abut, so that between the wings 27, 27', 27th and the pressure chambers can be pressurized with hydraulic oil in order to allow or prevent the rotor 23 from pivoting about the axis A; the.
  • the operation of a slewing motor is known per se and will therefore not be explained further here.
  • the wings 27, 27 'and 27 are rigidly connected in the illustrated embodiment with the rotor 23. In another embodiment, not shown, however, they can be arranged to be displaceable in slots provided in the rotor 23, wherein Spring forces and / or can be urged radially outwards against the housing 25 by hydraulic pressure. This principle is known from vane pumps.
  • the projections 29, 29 'and 29 may be formed as a locking slide, which are arranged displaceably in slots in the housing 25, wherein they can be urged by spring forces and / or by hydraulic pressure radially inwardly against the rotor 23 This principle is known from paddlewheel pumps.
  • both the wings 27, 27 ', 27 "as well as the projections 29, 29', 29" displaceable in slots or form as a barrier wing.
  • the rotor 23 has a - in cross-section - substantially triangular-shaped recess into which a likewise - im Seen cross section - substantially triangular portion of the eccentric 19 engages.
  • the rotor 23 and the eccentric 19 are rotatably connected to each other, so that the actuating element 21, so here the pivot motor, a pivoting of the eccentric 19 and thus a displacement of the piston pin 15 along a circular path about the axis A can cause.
  • the rotor 23 and the eccentric 19 are rotatably connected to one another by a toothing.
  • a toothing Of course, other possibilities of a rotationally fixed connection between these elements are possible.
  • Figure 2 shows a sectional view of the device 1, which is perpendicular to the image plane of Figure 1 and through the longitudinal axis of the Pleu- ice L1. Identical and functionally identical elements are provided with the same reference numerals, so that reference is made to the preceding description.
  • the axis A is shown in phantom by which the piston pin 15 along a circular path is displaced.
  • a longitudinal axis L2 of the Kobenbolzens 15 is shown in phantom.
  • the actuator 17 is at least partially disposed in the illustrated embodiment between two tabs 34, 34 'of the connecting rod 3, which form the upper connecting rod 5 and in particular the actuating element 21 engage around at least partially laterally.
  • the actuating device 17 may preferably also at least partially on one of the tabs 34, 34 ', wherein it is preferably arranged laterally on this.
  • the other flap 34, 34 'then preferably falls away, so that the upper connecting rod 5, the one flap 34 or 34' and the actuator 17 includes.
  • a single lobe 34 which is arranged symmetrically, preferably symmetrically with respect to the longitudinal axis L 1, wherein the actuating device 17 is arranged either in a clear recess of this lobe 34 or laterally thereon.
  • two actuators 17 may be provided laterally by tabs 34. All of these embodiments are encompassed by the formulation that the actuating device 17 is arranged in the upper connecting rod eye 5.
  • the piston pin 15 is formed integrally with the eccentric 19. In another embodiment, it may be provided that the piston pin 15 is mounted in the eccentric 19, wherein the two elements are not formed in one piece. It is only important that the piston pin 15 is arranged eccentrically in the eccentric 19.
  • FIG. 2 also shows that the eccentric 19 is pivotably mounted about the axis A in at least one bearing, in this case two bearings, preferably two plain bearings 35, 35 '. In other embodiments, not shown, the eccentric 19 may be pivotally mounted in at least one ball or roller bearings.
  • Partial region having - seen in cross section - is triangular in shape and in the - seen in cross section - triangular Recess of the rotor 23 engages, which in turn can be seen in Figure 1.
  • the actuating element 21, that is to say the swivel motor in the illustrated embodiment, is laterally encompassed by two side plates 37, 37 ', which simultaneously hold the swivel motor securely and the pressure chambers 31, 31', 31 "and the pressure chambers 31, 31 ', 31"
  • the side plates 37, 37 ' facing away from the actuating element 21, there are annular grooves 39, 39', through which the hydraulic oil is distributed to the various pressure chambers, for which through-bores are respectively provided to the pressure chambers through the side plates 37, 37 ' of which the bores 33, 33 ', 33 "are shown in FIG.
  • channels 41, 41 ' are formed, which serve to supply the swing motor with hydraulic oil or its outflow.
  • the channels 41, 41 ' extend in a first region substantially parallel to the longitudinal axis L1, wherein they open into holes in a second region, which are substantially perpendicular to this direction and the channels 41, 41' in fluid communication with the annular grooves 39, 39 'bring.
  • a valve 43 is provided with the aid of which the actuating device 17 can be activated by connecting the channels 41, 4V alternately with an oil supply or with an outflow.
  • annular groove 39 for example, the supply of the pressure chambers 31, 31 ', 31 "serves with hydraulic oil, while the annular groove 39' in this case the supply of the other, antagonistic to the pressure chambers 31, 31 ', 31st "acting pressure chambers is used.
  • the operation of the device 1 will be explained in more detail.
  • the illustrated embodiment of a device 1 is hydraulically activated.
  • the valve 43 is in its position shown in FIG. 2, the channel 41 'is connected to an oil supply while the channel 41 is connected to a drain.
  • the pressure chambers, not shown in FIG. 1, can therefore be supplied with hydraulic oil via the annular groove 39 ', while hydraulic oil can flow out of the pressure chambers 31, 31', 31 "via the channel 41.
  • the hydraulic activation of the actuating device 17 is thus responsive to the fact that the channels 41, 4V are connected to an oil supply or an outflow, so that a displacement of the rotor 23 and thus of the eccentric 19 can take place.
  • the pivoting motor ie the actuating element 21, causes a displacement of the eccentric 19 about the axis A 1 so that the piston pin 15 is also displaced along a circular path about this axis.
  • Hydraulic activation does not mean that this displacement is caused by the pressure of the hydraulic oil. It is merely released a fluid path for the hydraulic oil, so that a displacement is possible, which is driven by, for example, by mass and / or gas forces.
  • the actuator hydraulically.
  • the pressure of the hydraulic oil is used to cause a displacement of the rotor 23 and ultimately the piston pin 15.
  • the displacement can take place independently of the mass and / or gas forces occurring during the working cycle of the piston. This has the advantage, in particular, that a displacement can take place rapidly, while it is shown that a displacement with the aid of the mass and / or gas forces requires several working cycles of the piston.
  • the maximum or minimum connecting rod length is defined in each case by a stop of the wings 27, 27 ', 27 "on the projections 29, 29', 29".
  • it is possible to increase or decrease the length of the piezo for example by displacing the stops, until the diameter line D3 with the longitudinal axis L1 in the upper or lower Ren position of the piston pin 15 comes to cover. This is especially advantageous if only a comparatively low hydraulic pressure for holding the position of the piston pin 15 is available. In this case, mass and / or gas forces are essentially absorbed by the connecting rod 3, so that a small holding pressure is sufficient to counteract a displacement of the piston pin 15.
  • the valve 43 serves to control the actuating device 17, that is to say for its hydraulic activation, fixing and / or for driving the same, if this is to be hydraulically driven. It is therefore designed so that it can connect the channels 41, 41 'alternately with an oil supply or an outflow, preferably also can block both channels.
  • both channels 41, 4V must be lockable at the same time.
  • the valve 43 must therefore have a third functional position, in which both channels 41, 41 'are connected neither to the oil supply nor to an outflow.
  • the current functional position of the valve 43 is preferably predetermined by a control loop, which comprises at least one knock sensor. It is then possible to select the connecting rod length and thus the compression ratio in preferably each operating state of the engine so that it is virtually driven at the knock limit, that is, has a compression ratio in which just no knocking combustion occurs. This ensures that the best possible efficiency is always achieved.
  • a higher oil pressure is used for a hydraulic drive of the actuating device 17 than is the case with a purely hydraulic activation.
  • Connecting rod 5 is arranged. This allows the device 1 and in particular the connecting rod 3 have a compact design, and the movable masses are compared to known Reduced devices, so that the resulting loss of power of the engine is minimized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un dispositif (1) destiné à faire varier le rapport de compression dans un moteur à combustion interne, avec une bielle (3) qui est articulée par la tête de bielle (9) à un vilebrequin et par le pied de bielle (5) à un piston (7), avec un axe de piston (15) qui est monté de manière pivotante dans le piston (7) et de manière excentrique dans le pied de bielle (5) et qui peut se déplacer sur une trajectoire circulaire autour d'un axe central (A) du pied de bielle (5), la longueur de la bielle, mesurée entre un axe central de la tête de bielle (9) et un axe central de l'axe de piston (15), pouvant être réglée par un déplacement de l'axe de piston (15) monté excentrique, et avec un dispositif d'actionnement (17) pour déplacer l'axe de piston (15).
PCT/EP2010/001191 2009-03-26 2010-02-26 Dispositif destiné à faire varier le rapport de compression dans un moteur à combustion interne WO2010108582A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112010001349T DE112010001349A5 (de) 2009-03-26 2010-02-26 Vorrichtung zur Veränderung des Verdichtungsverhältnisses in einem Verbrennungsmotor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009015979 2009-03-26
DE102009015979.7 2009-03-26

Publications (1)

Publication Number Publication Date
WO2010108582A1 true WO2010108582A1 (fr) 2010-09-30

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Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010061361A1 (de) * 2010-12-20 2012-04-26 Dr.Ing.H.C. F. Porsche Ag Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061363A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061362A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil
DE102011002138A1 (de) * 2011-04-18 2012-10-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verstellbare Pleuelstangenvorrichtung für eine Brennkraftmaschine und Brennkraftmaschine mit einer derartigen verstellbaren Pleuelstangenvorrichtung
AT511803B1 (de) * 2011-12-23 2013-03-15 Avl List Gmbh Pleuelstange für eine hubkolbenmaschine
DE102012112434A1 (de) * 2012-12-17 2014-06-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstangenanordnung sowie Verfahren zum Entlüften eines Hydraulikzylinders einer derartigen Pleuelstangenanordnung
WO2014162043A1 (fr) * 2013-04-03 2014-10-09 Wärtsilä Finland Oy Agencement pour le réglage du taux de compression d'un moteur à piston à combustion interne
DE102013105391A1 (de) * 2013-05-27 2014-11-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem solchen Umschaltventil
DE102014100585A1 (de) * 2014-01-20 2015-01-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
DE102013014090A1 (de) * 2013-08-27 2015-03-05 Dr. Ing. H.C. F. Porsche Ag Verbrennungsmotor und Pleuelstange
WO2015074649A1 (fr) * 2013-11-21 2015-05-28 Schaeffler Technologies AG & Co. KG Dispositif pour faire varier le taux de compression d'une unité de cylindre d'un moteur à combustion interne à piston alternatif
DE102014101929A1 (de) * 2014-02-17 2015-09-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
EP2991675A1 (fr) 2013-04-05 2016-03-09 The Governors of the University of Alberta Vaccin campylobacter
DE102015121915A1 (de) * 2015-12-16 2017-06-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
FR3051857A1 (fr) * 2016-05-24 2017-12-01 Renault Sas Bielle pour moteur a combustion a taux de compression variable et systeme motopropulseur correspondant
DE102016113640A1 (de) 2016-07-25 2018-01-25 Hilite Germany Gmbh Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
DE102016113646A1 (de) 2016-07-25 2018-01-25 Hilite Germany Gmbh Exzenter-Verstelleinrichtung zur Verstellung einer effektiven Pleuellänge eines Pleuels einer Brennkraftmaschine
DE102017107682A1 (de) 2016-08-16 2018-02-22 ECO Holding 1 GmbH Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
DE102016115765A1 (de) 2016-08-25 2018-03-01 Pierburg Gmbh Kolben und Vorrichtung zur Veränderung des Verdichtungsverhältnisses
AT519149A1 (de) * 2016-09-30 2018-04-15 Avl List Gmbh Längenverstellbares Pleuel mit Steuerungseinrichtung
US20210332747A1 (en) * 2020-04-23 2021-10-28 FEV Group GmbH Connecting rod for changing a compression ratio of an internal combustion engine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2427668A (en) * 1945-09-01 1947-09-23 Peter L Gill Variable compression engine
SU661128A1 (ru) * 1977-02-14 1979-05-07 Головное Специализированное Конструкторское Бюро По Двигателям Средней Мощности Двигатель внутреннего сгорани
WO2007043093A1 (fr) * 2005-10-14 2007-04-19 Hipass Srl Regulateur automatique du taux de compression pour moteurs a explosion
DE102005055199A1 (de) * 2005-11-19 2007-05-24 Fev Motorentechnik Gmbh Hubkolbenverbrennungskraftmaschine mit einstellbar veränderbarem Verdichtungsverhältnis
EP2006509A2 (fr) * 2007-06-22 2008-12-24 Michael Von Mayenburg Moteur à combustion interne doté d'un taux de compression variable

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2427668A (en) * 1945-09-01 1947-09-23 Peter L Gill Variable compression engine
SU661128A1 (ru) * 1977-02-14 1979-05-07 Головное Специализированное Конструкторское Бюро По Двигателям Средней Мощности Двигатель внутреннего сгорани
WO2007043093A1 (fr) * 2005-10-14 2007-04-19 Hipass Srl Regulateur automatique du taux de compression pour moteurs a explosion
DE102005055199A1 (de) * 2005-11-19 2007-05-24 Fev Motorentechnik Gmbh Hubkolbenverbrennungskraftmaschine mit einstellbar veränderbarem Verdichtungsverhältnis
EP2006509A2 (fr) * 2007-06-22 2008-12-24 Michael Von Mayenburg Moteur à combustion interne doté d'un taux de compression variable

Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010061361A1 (de) * 2010-12-20 2012-04-26 Dr.Ing.H.C. F. Porsche Ag Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061363A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061362A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil
DE102010061362B4 (de) 2010-12-20 2022-12-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil
DE102010061363B4 (de) 2010-12-20 2023-09-28 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061361B8 (de) 2010-12-20 2022-05-12 Dr.Ing.H.C. F. Porsche Ag Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102010061361B4 (de) 2010-12-20 2022-04-14 Dr.Ing.H.C. F. Porsche Ag Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil sowie Verfahren zur Steuerung des Umschaltventils
DE102011002138A1 (de) * 2011-04-18 2012-10-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verstellbare Pleuelstangenvorrichtung für eine Brennkraftmaschine und Brennkraftmaschine mit einer derartigen verstellbaren Pleuelstangenvorrichtung
AT511803B1 (de) * 2011-12-23 2013-03-15 Avl List Gmbh Pleuelstange für eine hubkolbenmaschine
AT512334A1 (de) * 2011-12-23 2013-07-15 Avl List Gmbh Längenverstellbare Pleuelstange
AT511803A4 (de) * 2011-12-23 2013-03-15 Avl List Gmbh Pleuelstange für eine hubkolbenmaschine
DE102012112434A1 (de) * 2012-12-17 2014-06-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstangenanordnung sowie Verfahren zum Entlüften eines Hydraulikzylinders einer derartigen Pleuelstangenanordnung
DE102012112434B4 (de) 2012-12-17 2022-10-20 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstangenanordnung sowie Verfahren zum Entlüften eines Hydraulikzylinders einer derartigen Pleuelstangenanordnung
WO2014162043A1 (fr) * 2013-04-03 2014-10-09 Wärtsilä Finland Oy Agencement pour le réglage du taux de compression d'un moteur à piston à combustion interne
EP2991675A1 (fr) 2013-04-05 2016-03-09 The Governors of the University of Alberta Vaccin campylobacter
DE102013105391A1 (de) * 2013-05-27 2014-11-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem solchen Umschaltventil
DE102013105391B4 (de) 2013-05-27 2021-12-23 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem solchen Umschaltventil
DE102013014090A1 (de) * 2013-08-27 2015-03-05 Dr. Ing. H.C. F. Porsche Ag Verbrennungsmotor und Pleuelstange
US9567901B2 (en) 2013-08-27 2017-02-14 Hilite Germany Gmbh Internal combustion engine and connecting rod
WO2015074649A1 (fr) * 2013-11-21 2015-05-28 Schaeffler Technologies AG & Co. KG Dispositif pour faire varier le taux de compression d'une unité de cylindre d'un moteur à combustion interne à piston alternatif
US9567902B2 (en) 2014-01-20 2017-02-14 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Connecting rod and internal combustion engine
DE102014100585A1 (de) * 2014-01-20 2015-01-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
US9726077B2 (en) 2014-02-17 2017-08-08 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Connecting rod and internal combustion engine
DE102014101929A1 (de) * 2014-02-17 2015-09-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
DE102014101929B4 (de) 2014-02-17 2022-02-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
DE102015121915B4 (de) * 2015-12-16 2021-04-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange mit einer Exzenter-Verstelleinrichtung und ein Verbrennungsmotor
DE102015121915A1 (de) * 2015-12-16 2017-06-22 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstange und Verbrennungsmotor
FR3051857A1 (fr) * 2016-05-24 2017-12-01 Renault Sas Bielle pour moteur a combustion a taux de compression variable et systeme motopropulseur correspondant
WO2018019515A1 (fr) 2016-07-25 2018-02-01 ECO Holding 1 GmbH Dispositif de réglage à excentrique permettant de régler une longueur effective d'une bielle d'un moteur à combustion interne
DE102016113646B4 (de) 2016-07-25 2020-04-23 Hilite Germany Gmbh Exzenter-Verstelleinrichtung zur Verstellung einer effektiven Pleuellänge eines Pleuels einer Brennkraftmaschine
WO2018019514A1 (fr) 2016-07-25 2018-02-01 ECO Holding 1 GmbH Bielle pour un moteur à combustion interne à compression variable
DE102016113646A1 (de) 2016-07-25 2018-01-25 Hilite Germany Gmbh Exzenter-Verstelleinrichtung zur Verstellung einer effektiven Pleuellänge eines Pleuels einer Brennkraftmaschine
DE102016113640A1 (de) 2016-07-25 2018-01-25 Hilite Germany Gmbh Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
WO2018033276A1 (fr) 2016-08-16 2018-02-22 ECO Holding 1 GmbH Bielle pour un moteur à combustion interne à compression variable
DE102017107682A1 (de) 2016-08-16 2018-02-22 ECO Holding 1 GmbH Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
DE102016115765A1 (de) 2016-08-25 2018-03-01 Pierburg Gmbh Kolben und Vorrichtung zur Veränderung des Verdichtungsverhältnisses
US11066988B2 (en) 2016-09-30 2021-07-20 Avl List Gmbh Length-adjustable connecting rod with control device
AT519149B1 (de) * 2016-09-30 2018-11-15 Avl List Gmbh Längenverstellbares Pleuel mit Steuerungseinrichtung
AT519149A1 (de) * 2016-09-30 2018-04-15 Avl List Gmbh Längenverstellbares Pleuel mit Steuerungseinrichtung
US20210332747A1 (en) * 2020-04-23 2021-10-28 FEV Group GmbH Connecting rod for changing a compression ratio of an internal combustion engine
US11635019B2 (en) * 2020-04-23 2023-04-25 FEV Group GmbH Connecting rod for changing a compression ratio of an internal combustion engine

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