WO2017045667A1 - Moteur à pistons alternatifs à taux de compression variable, et procédé permettant de modifier le taux de compression d'un moteur à pistons alternatifs - Google Patents

Moteur à pistons alternatifs à taux de compression variable, et procédé permettant de modifier le taux de compression d'un moteur à pistons alternatifs Download PDF

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Publication number
WO2017045667A1
WO2017045667A1 PCT/DE2016/100422 DE2016100422W WO2017045667A1 WO 2017045667 A1 WO2017045667 A1 WO 2017045667A1 DE 2016100422 W DE2016100422 W DE 2016100422W WO 2017045667 A1 WO2017045667 A1 WO 2017045667A1
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WO
WIPO (PCT)
Prior art keywords
piston
support
connecting rod
working space
cylinder
Prior art date
Application number
PCT/DE2016/100422
Other languages
German (de)
English (en)
Inventor
Uwe Schaffrath
Mike Souren
Andre Prinz
Original Assignee
Fev 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 Fev Gmbh filed Critical Fev Gmbh
Priority to DE112016004197.7T priority Critical patent/DE112016004197A5/de
Publication of WO2017045667A1 publication Critical patent/WO2017045667A1/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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • 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
    • 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof

Definitions

  • the invention relates to a reciprocating engine with variable compression ratio, wherein it is in particular a reciprocating internal combustion engine in the reciprocating piston engine. Furthermore, the invention relates to a method for changing the compression ratio of a reciprocating piston engine, in particular a reciprocating internal combustion engine.
  • Reciprocating engines and in particular reciprocating internal combustion engines with variable compression ratio are known in principle. Their advantages are to be seen in particular in an increased efficiency.
  • the connecting rod with compression piston As an engine component that is changeable to adjust the compression ratio, in particular the connecting rod with compression piston as proved appropriate.
  • the effective connecting rod length and thus the compression ratio can be changed.
  • gas and mass forces act on the compression piston.
  • the gas forces arise during the expansion of the gas-fuel mixture. These forces press the compression piston against the connecting rod.
  • eccentric mounting of the compression piston relative to the longitudinal axis of the connecting rod can be achieved that these gas forces move the compression piston in the direction of the connecting rod. In this way the compression ratio can be changed from high values to low values. If this is not desired, namely because the reciprocating engine is to be operated at a high compression ratio, the adjusting element is locked for the compression piston, which is done for example by a cylinder / piston support unit.
  • the compression ratio can be changed from low to high values.
  • the accelerations are used, which act on the compression piston when it passes through its top dead center.
  • a movement of the compression piston in these phases can in turn be prevented by a cylinder / piston support unit which acts on the adjusting element for the compression piston.
  • one and the same cylinder / piston support unit is designed for both functions; such a support unit operates with a double-acting support piston.
  • the support unit is operated hydraulically, preferably not actively, but passively by either hydraulic fluid is sucked into the working space or from the working space as a result of induced by the forces described above displacement of the support piston within the support cylinder Support piston is displaced.
  • VCR reciprocating engine with variable compression ratio
  • hydraulic fluid is displaced from the working space of a support cylinder, as a result of a displacement of the support piston, which in turn is the result of forces acting on the compression piston.
  • the hydraulic fluid is "pumped", so to speak, whereby the flow resistance should be as low as possible.
  • the object of the invention is a reciprocating engine with variable compression ratio and a method for changing the compression ratio of such a reciprocating engine, in particular a reciprocating internal combustion engine proposed, which is provided with
  • a rotatably mounted crankshaft arranged in the housing, at least one connecting rod, which is rotatably mounted on the crankshaft by means of a crankshaft bearing having a lubricant path, wherein the connecting rod carries a compression piston, which is bidirectionally movably guided in a cylinder formed in the housing, and an adjusting mechanism for adjusting the compression piston relative to the connecting rod for the purpose of changing the compression ratio, wherein the adjusting mechanism comprises an adjusting element for displacing the compression piston relative to the connecting rod and at least one cylinder / piston support unit with a support cylinder and a support piston guided displaceably in this, which in operative connection with the adjusting element stands,
  • the support cylinder has at least one work space which can be filled with a substantially incompressible fluid, in particular oil, which can optionally be introduced into the work space or can be discharged from the work space, and
  • This reciprocating engine is inventively characterized in that the connecting rod has a flow channel extending from the at least one working chamber of the support cylinder, which can be brought into fluid communication with a discharge opening arranged in the outer surface of the connecting rod for discharging fluid from the at least one working space into the housing.
  • the connecting rod comprises the actual Pleuel Sciences and arranged on / in this parts, which define as the Pleuel Sciences the outer surface of the connecting rod in the context of the invention.
  • a connecting rod for a reciprocating engine with variable compression ratio in particular for a reciprocating internal combustion engine, a housing, a housing disposed in the rotatably mounted crankshaft, at least one cylinder formed in the housing and a bidirectionally movable in the cylinder Compression piston, wherein the connecting rod is provided with
  • crankshaft bearing for rotatably supporting the connecting rod body on the crankshaft, wherein the crankshaft bearing has a lubricant path
  • the adjusting mechanism has an adjusting element for displacing the compacting piston bearing relative to the connecting rod body and at least one cylinder / piston supporting unit with a supporting cylinder and a support piston displaceably guided in this, which is in operative connection with the adjusting element,
  • the support cylinder has at least one work space which can be filled with a substantially incompressible fluid, in particular oil, which can optionally be introduced into the work space or can be discharged from the work space, and
  • the connecting rod is characterized in that the connecting rod body has a flow channel extending from the at least one working space of the support cylinder, which can be brought into fluid communication with an outlet opening arranged in the outer surface of the connecting rod body for discharging fluid from the at least one working space into the housing ,
  • the connecting rod body also includes parts arranged in / on it, which, like the connecting rod body, define the outer surface thereof in the sense of the invention.
  • the above object is also achieved by a method for changing the compression ratio of a reciprocating engine, in particular a reciprocating internal combustion engine, with variable compression ratio as described above and / or with at least one connecting rod, also as described above, wherein the fluid from the at least one Working space of the at least one support cylinder for the purpose of changing the compression ratio is discharged directly into the housing of the reciprocating engine.
  • the hydraulic fluid which is removed during displacement of the support piston from the working space of the support cylinder, is discharged directly into the housing of the reciprocating engine.
  • the flow resistance is as low as possible, since the drained hydraulic fluid no changeover valves or the like. must flow through the flow resistance increasing fluidic elements.
  • the "hydraulic fluid" pressed out of a support cylinder in particular engine oil, is discharged freely into the oil sump of the reciprocating engine, while the engine oil to be supplied to the working space or into the working chamber of the support cylinder is completely removed from the oil circuit, and as a rule from the crankshaft connecting rod bearing.
  • the oil can also be taken from another bearing, which is lubricated and cooled with the engine oil. If sufficient oil can be supplied from the respective bearing, thereby the adjustment of the compression piston is accomplished faster than in known systems, since the pressure difference for the dissipated oil while higher and the flow resistance is lower than when the oil is dissipate against the oil pressure, as in the known so far with "closed" hydraulic circuit operating systems is the case.
  • the working space of a support cylinder is associated with a supply channel and a discharge channel, both of which open into the working space of the support cylinder.
  • the supply and removal of hydraulic fluid into and out of the working space should be carried out expediently only during the adjustment phases for changing the compression ratio.
  • the discharge channel can be brought into fluid communication with an outlet opening arranged on the outer surface of the connecting rod, which is provided according to the invention for adjusting the compression ratio, a fluid connection exists between the inlet and outlet channels via the working space of the support cylinder.
  • the inlet channel is the current hydraulic fluid pressure, for example, the current engine oil pressure. Hydraulic fluid thus flows into the working chamber of the support cylinder via the inlet channel in order to immediately discharge into the housing via its outlet channel.
  • the support piston in a displacement position, the one of at least two adjustable compression ratios, the inlet channel blocked with respect to the flow channel.
  • the support piston In this Sliding position, the support piston is preferably not supported against a hydraulic fluid in the working space of the support cylinder, but directly from the bottom of the working space.
  • the support piston acts in this situation as a blocking or blocking element to interrupt the "light" fluid connection of inlet and outlet channel.
  • the support piston of the at least one or each cylinder / piston support unit has a circumferential sealing element for sealing the working space of the support cylinder and that the circumferential sealing element in a displacement position corresponding to one of at least two adjustable compression ratios, the Blocked fluid communication between the inlet and outlet channel in the working space of the support cylinder, and in particular closes the mouth of the inlet and / or the discharge channel in the working space of the support cylinder.
  • the support piston has at least one or each cylinder / piston support unit at its the bottom of the working space of the support cylinder end facing a sealing element, wherein the inlet and / or outlet channel on the ground and / or at the side wall of the support cylinder open into the working space and wherein the sealing element in a displacement position corresponding to one of at least two adjustable compression ratios, the fluid communication between inlet and outlet channel blocked in the working space of the support cylinder, in particular the mouth of the inlet and / or the drainage channel closes in the working space of the support cylinder.
  • the sealing element is annular and in particular an O-ring and / or that the sealing element is a lamellar sealing element or operates in the manner of a lamellar seal and / or that the sealing element is plate-shaped.
  • FIGS. 25 to 28 are the individual phases of the relative displacement of the compression piston relative to the connecting rod using a first embodiment of a switching valve according to a second embodiment for releasing or blocking or blocking the inflow and outflow of hydraulic oil from or into the working spaces of two cylinder piston support units and FIGS. 25 to 28
  • the internal combustion engine 10 has a housing 12, in which at least one cylinder 14 is formed.
  • a compression piston 16 which is mounted on a connecting rod 18 moves.
  • the combustion chamber 20 Above the compression piston 16 is the combustion chamber 20, into which an inlet channel and an outlet channel 24 open.
  • the ignition device for the air-fuel mixture is shown in FIGS. not shown.
  • the connecting rod 18 is moved in a known manner by a crankshaft 26.
  • This crankshaft 26 has counterweights 28 with crank pins 30, on which the individual connecting rods 18 are mounted.
  • the Kurbelwellenpleuellager 32 is acted upon in a known manner with pressurized engine oil and has a lubricant path 33.
  • the corresponding lubricant system has a pump 34, which sucks engine oil from the oil sump 36 of the housing 12.
  • the engine oil also serves to cool, for example, the bearings of the internal combustion engine 10.
  • a (for example eccentric) adjusting element 38 in the form of an adjusting lever 39, which is pivotably mounted on the connecting rod 18.
  • the pin 42 Eccentrically to the pivot point 40 of the adjusting element 38, the pin 42 is mounted, which carries the compression piston 16. The center of the pin 42 is shown at 44.
  • the adjusting lever 39 has a first end 46 and a remote from this second end 48, on each of which piston rods 50, 52 are articulated.
  • the piston rods 50, 52 are part of two cylinder / piston support units 54, 56, of which the first support unit 54 has a first support cylinder 58 formed in the connecting rod 18 with a displaceably guided in this first support piston 60, while the second support unit 56 has a second support cylinder 62 having guided in this second support piston 64.
  • These two support units 54, 56 serve to lock the adjusting element 38 in its two Maximalverschwenkpositionen, in each of which another of the two support piston 60, 64 abuts the bottom 66 and 68 of the respective support cylinder 58 and 62 respectively.
  • the working space 70 and 72 flows into or out of the hydraulic fluid when the compression ratio is adjusted.
  • an inlet channel 74 or 76 and an outlet channel 78 or 80 open into each of the two working chambers 70, 72.
  • a hydraulic circuit with, for example, throttles or orifices 82, 84, check valves 86, 88 and a changeover valve 90, the two working chambers 70, 72 interconnected, so that the desired adjustment of the compression ratio can be made from a high to a low value or vice versa ,
  • the hydraulic circuit is via the channel 92 with the connecting rod bearing 32 and thus with the
  • Lubricant path 33 of the connecting rod bearing 32 is connected.
  • the hydraulic circuit is ultimately supplied with engine oil.
  • the switching valve 90 is a 2/3-way valve, ie a valve that can assume two switching positions and has three connections. The three connections are in the two switch positions in different Licher manner interconnected or blocked with each other.
  • the actuation of the switching valve 90 for example, mechanically, electrically, magnetically or hydraulically, and indeed whenever the compression ratio is to be changed from one value to the other value.
  • the constructive solution for adjusting the switching valve 90 is not the subject of the invention and will therefore not be further described here. Examples of related constructions are described in WO 2014/019683 AI and WO 2014/019684 AI.
  • the switching valve 90 is in the position in which the compression ratio can be changed from a high to a low value.
  • the starting point is Fig. 1; the compression ratio is maximum in this case, which means that the compression piston 16 has its greatest possible distance from the connecting rod 18.
  • the second support piston 64 abuts the bottom 68 of the second support cylinder 62, while the support piston 60 is supported in the support cylinder 58 on an oil pad, since the working space 70 of the support cylinder 58 is filled with engine oil.
  • engine oil may be forced out of the working space 70 thereof as a result of displacement of the first support piston 60 into the first support cylinder 58, as a result of displacement of the first support piston 60, the second support piston 64 moves away from the bottom 68 of the second support cylinder 62 and thus Engine oil is sucked into the second support cylinder.
  • a reverse engine oil flow is excluded by the hydraulic circuit and as a result of taking the first position of the switching valve 90.
  • Fig. 1 shows the situation immediately prior to ignition of the compressed air in the combustion chamber 20 air-fuel mixture.
  • gas forces act on the compression piston 16, which lead to a rotation of the adjusting element 38 in the direction of the arrow 96 when the discharge channel 78 is released.
  • the compression piston 16 has reached its bottom dead center (see FIG. 2), the first support piston 60 is already further in the first Workspace 70 of the first support cylinder 58 immersed, while the second support piston 64 has moved away from the bottom 68 of the second support cylinder 62 while hydraulic fluid passes into its working space 72.
  • FIG. 2 shows the situation immediately prior to ignition of the compressed air in the combustion chamber 20 air-fuel mixture.
  • FIG. 3 shows the situation when compression piston 16 returns to its top dead center at the end of the exhaust stroke, from which point it returns to its bottom dead center during the intake stroke, as shown in FIG. In this phase, no gas forces acting on the compression piston, which could move this relative to the connecting rod 18. At most, at or shortly after passing through the bottom dead center (FIG. 2), mass forces acting on the compression piston 16 may act on the compression piston 16 against the connecting rod 18.
  • FIGS. 7 to 12 individual phases of two successive operating cycles of the internal combustion engine 10 are shown, which are used to increase the compression ratio from the low value set according to FIG. 6 to the high value according to FIG. 12 or FIG adjust.
  • the switching valve 90 assumes its second position, in the engine oil from the second working space 72 can be discharged, while engine oil in the first working space 70 is introduced einaugbar.
  • the removal of engine oil from the second working space 72 takes place as a result of the (further) in the second support cylinder 62 advancing second support piston 64, which means that at the same time the first support piston 60 moves away from the bottom 66 of the first support cylinder 58 and sucks engine oil, so to speak.
  • In the second position of the change-over valve 90 only this direction of engine oil transfer is possible; Backflow of engine oil is excluded by the hydraulic circuit.
  • the adjusting forces resulting from the inertial forces are significantly lower than the adjusting forces resulting from the gas forces.
  • the adjustment of the compression ratio from a small value to a large value is thus much more critical than the adjustment of a large compression ratio to a small compression ratio.
  • the engine oil forced out of the second support cylinder 62 when adjusting from small to large compression ratio is discharged directly into the housing 12 of the internal combustion engine 10 and thus into the oil sump 36. This is shown in FIGS. 7 to 12 shown. In the embodiment according to FIGS.
  • FIGS. 13 to 24 is therefore a variant of the hydraulic circuit with respect to FIGS. 1 to 12 alternatively ausgestaltetem switching valve 90 'shown.
  • the switching valve 90 ' is designed as a 2/4-way valve, it being possible to discharge engine oil directly into the housing via one of the valve connections, while it is fed directly to the hydraulic circuit via another connection.
  • the situations according to FIGS. 13 to 18 corresponds to those in FIGS. 1 to 6 shown situations.
  • the second support piston 64 has a piston ring in the form of a peripheral sealing element 100, via which the second working space 72 in the second support cylinder 62 is sealed. Until the end position of the support piston 64, in which this rests against the bottom wall 68 of the second support cylinder 62, the fluid connection between the inlet channel 76 and the outlet channel 80 is maintained. When at the bottom 68 of the first support cylinder 62 adjacent second support piston 64 now closes the peripheral sealing element 100, the mouth opening 102 of the drain passage 80. The situation could also be realized vice versa, namely the mouth opening 104 of the inlet channel 76 is closed by the circumferential sealing element 100 ,
  • FIG. 26 shows an embodiment for the obstruction of the fluid connection between the inlet channel 76 and the outlet channel 80 in the form of a labyrinth seal 105.
  • an annular recess 108 is incorporated in the end face 106 of the second supporting piston 64 facing the bottom 68 of the second supporting cylinder 62 in which a protruding from the bottom 68 annular projection 110 is immersed when the second support piston 64 rests against the bottom 68 of the second support cylinder 62.
  • annular recess 108 in the second support piston 64, a plurality of preferably concentrically arranged annular recesses 108 may be provided, in which case a plurality of preferably concentric, annular projections 110 also project from the bottom 68 of the second support cylinder 62. By this labyrinth seal the fluid connection between inlet channel 76 and outlet channel 80 is blocked.
  • the depression 108 in the second support piston 64 and the projection 110 at the bottom of the second support cylinder 62 are formed. It should be mentioned at this point that the situation is also possible the other way round or that with several recesses and projections these alternately in the second support cylinder 62 and in the second th support piston 64 may be arranged. It is crucial that through the interaction of recess and projection, there is a constriction and extension of the fluid connection between inlet channel 76 and outlet channel 80, whereby the desired sealing effect is achieved.
  • a sealing element 112 and 114 are arranged, which obstruct either the mouth opening 104 of the inlet channel 76 or the mouth opening 102 of the drain channel 80 on all sides.
  • the sealing element is an O-ring
  • the sealing element 114 of the exemplary embodiment according to FIG. 28 is a plate, disk, block, strip or the like. is trained. While according to FIG. 28 the sealing element 114 closes the inlet opening 104 or 102 (depending on the embodiment), in the embodiment according to FIG. 27 the corresponding opening remains unlocked, whereby, however, the fluid connection to the respective other opening is obstructed by the sealing element 112.
  • the invention has been described above with reference to a VCR reciprocating engine in which the effective length of the connecting rod is changed to adjust the compression ratio. It should be emphasized at this point that the invention is not limited to such VCR reciprocating engines. Rather, the invention is generally applicable to the hydraulic adjustment of an engine component utilizing the forces acting on the engine component during operation. It is also possible that the adjustment of the compression ratio is supported by variation of the oil pressure.
  • the compression ratio can be actively or passively set for all cylinders of the internal combustion engine, for all cylinders of a cylinder bank of the internal combustion engine and / or for the individual cylinders of the internal combustion engine.
  • preference is given to the geometry of an engine component such as, for example, the connecting rod length, the Crankshaft radius, the bearing of the crankshaft and / or the storage of the compression piston on the connecting rod and thus changed the effective connecting rod length.
  • This is preferably done hydraulically, ie using a medium.
  • the motor oil is especially suitable as a medium.
  • the active adjustment means that an adjustment of the relevant engine component is achieved by the action of external adjusting forces on the adjusting mechanism.
  • the passive adjustment means that acting on the engine component during operation of the internal combustion engine forces such as the gas pressure forces and the inertial forces are utilized to effect an adjustment of the engine component.
  • passive adjustment due to the utilization of these forces, an automatic adjustment of the engine component takes place, while in the active adjustment from the outside, ie in addition to the aforementioned acting forces or independently thereof, further adjusting forces are introduced.

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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 moteur à pistons alternatifs (10) muni d'un vilebrequin (26) agencé rotatif dans un carter (12) et d'au moins une bielle (18) qui est montée rotative au niveau du vilebrequin (26) au moyen d'un palier de vilebrequin (32) présentant un trajet de lubrifiant (33). La bielle (18) porte un piston de compression (16) qui est guidé mobile dans deux directions dans un cylindre (14) réalisé dans le carter (12). Le moteur à pistons alternatifs présente par ailleurs un mécanisme de déplacement permettant de déplacer le piston de compression (16) par rapport à la bielle (18) pour modifier le taux de compression, le mécanisme de déplacement présentant un élément de déplacement (38) servant à déplacer le piston de compression (16) par rapport à la bielle (18) et au moins une unité d'appui cylindre/piston (54, 56)) munie d'un cylindre d'appui (58, 62) dans lequel un piston d'appui (60, 64) est guidé de manière mobile et se trouve en liaison fonctionnelle avec l'élément de déplacement (38). Par ailleurs, l'espace de travail (70, 72) est en communication fluidique avec le trajet de lubrifiant (33) du palier de vilebrequin de la bielle (18) par l'intermédiaire d'un conduit d'amenée (74, 76), la bielle (18) présentant un conduit de sortie (78, 80) qui s'étend à partir du ou des espaces de travail (70, 72) du cylindre d'appui (58, 62) et qui peut être mis en communication fluidique avec une ouverture d'échappement ménagée dans la surface extérieure de la bielle (18) pour l'évacuation du fluide hors du ou des espaces de travail (70, 72) dans le carter (12).
PCT/DE2016/100422 2015-09-16 2016-09-12 Moteur à pistons alternatifs à taux de compression variable, et procédé permettant de modifier le taux de compression d'un moteur à pistons alternatifs WO2017045667A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112016004197.7T DE112016004197A5 (de) 2015-09-16 2016-09-12 Hubkolbenmaschine mit variablem Verdichtungsverhältnis und Verfahren zur Veränderung des Verdichtungsverhältnisses einer Hubkolbenmaschine

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Application Number Priority Date Filing Date Title
DE102015217725.4 2015-09-16
DE102015217725 2015-09-16

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WO2017045667A1 true WO2017045667A1 (fr) 2017-03-23

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3148193A1 (de) * 1981-12-05 1983-06-09 Daimler-Benz Ag, 7000 Stuttgart "kolbenbrennkraftmaschine mit veraenderlichem verdichtungsverhaeltnis"
DE102005055199A1 (de) * 2005-11-19 2007-05-24 Fev Motorentechnik Gmbh Hubkolbenverbrennungskraftmaschine mit einstellbar veränderbarem Verdichtungsverhältnis
DE102010061360A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil
DE102011056298A1 (de) * 2011-12-12 2013-06-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstangenanordnung sowie Verfahren zum Schalten eines Umschaltventils einer derartigen Pleuelstangenanordnung
WO2014019683A1 (fr) 2012-07-30 2014-02-06 Fev Gmbh Roue libre hydraulique pour moteur à combustion interne à rapport de compression variable
WO2014019684A1 (fr) 2012-07-30 2014-02-06 Fev Gmbh Unité d'actionnement pour composants de mécanisme moteur variables
DE102012107868A1 (de) * 2012-08-27 2014-02-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Vorrichtung und Verfahren zum Steuern eines Hydraulikflüssigkeitsstroms sowie Verbrennungsmotor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3148193A1 (de) * 1981-12-05 1983-06-09 Daimler-Benz Ag, 7000 Stuttgart "kolbenbrennkraftmaschine mit veraenderlichem verdichtungsverhaeltnis"
DE102005055199A1 (de) * 2005-11-19 2007-05-24 Fev Motorentechnik Gmbh Hubkolbenverbrennungskraftmaschine mit einstellbar veränderbarem Verdichtungsverhältnis
DE102010061360A1 (de) * 2010-12-20 2012-06-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem derartigen Umschaltventil
DE102011056298A1 (de) * 2011-12-12 2013-06-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pleuelstangenanordnung sowie Verfahren zum Schalten eines Umschaltventils einer derartigen Pleuelstangenanordnung
WO2014019683A1 (fr) 2012-07-30 2014-02-06 Fev Gmbh Roue libre hydraulique pour moteur à combustion interne à rapport de compression variable
WO2014019684A1 (fr) 2012-07-30 2014-02-06 Fev Gmbh Unité d'actionnement pour composants de mécanisme moteur variables
DE102012107868A1 (de) * 2012-08-27 2014-02-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Vorrichtung und Verfahren zum Steuern eines Hydraulikflüssigkeitsstroms sowie Verbrennungsmotor

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