WO2011107131A1 - Moteur à piston alternatif - Google Patents

Moteur à piston alternatif Download PDF

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Publication number
WO2011107131A1
WO2011107131A1 PCT/EP2010/007364 EP2010007364W WO2011107131A1 WO 2011107131 A1 WO2011107131 A1 WO 2011107131A1 EP 2010007364 W EP2010007364 W EP 2010007364W WO 2011107131 A1 WO2011107131 A1 WO 2011107131A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
reciprocating
adjusting device
engine according
reciprocating engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2010/007364
Other languages
German (de)
English (en)
Inventor
Tilmann RÖMHELD
Michael Wagenplast
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
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 Daimler AG filed Critical Daimler AG
Publication of WO2011107131A1 publication Critical patent/WO2011107131A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length

Definitions

  • the invention relates to a reciprocating engine specified in the preamble of claim 1 species and a reciprocating engine in the preamble of
  • Claim 12 specified type.
  • WO 2007/092168 A2 discloses an internal combustion engine with an adjustable compression ratio. To set the compression ratio is a
  • crankshaft of the internal combustion engine mounted on an eccentric carrier, whereby the position of the axis of rotation of the crankshaft in a crankcase of the
  • the eccentric carrier is actuated via a fork of a hydraulic actuator.
  • This internal combustion engine has further potential for representing efficient operation.
  • WO 02/12694 A1 discloses a reciprocating internal combustion engine with a displaceably arranged in a cylinder piston is known, which is articulated coupled with a connecting rod and whose movement is transferable to a crank of a crankshaft of the reciprocating internal combustion engine. Between the connecting rod and the crank, a transmission member is provided, the movement of which is manipulable via a control lever, with the aim of ensuring a controllable movement of the piston, in particular to allow a variation of the compression ratio. Also, this reciprocating internal combustion engine has potential for representing even more efficient operation.
  • a reciprocating internal combustion engine which also has a device for adjusting the compression ratio during operation.
  • This internal combustion engine has as a connection between the piston and the crankshaft to a rack, with their teeth on a gear or toothed segment unrolls, in turn, with its teeth on a
  • Rolling control rack and is rotatably mounted on a mounted on the crankshaft connecting rod.
  • the control rack is slidably mounted in the housing of the internal combustion engine in its longitudinal direction, so that by moving the
  • Control rack in the longitudinal direction the compression ratio can be changed.
  • the displacement of the control rack can be obtained, for example, hydraulically.
  • the high gas and mass forces of the reciprocating internal combustion engine require a very robust toothing and can expect a strong noise and lack of durability.
  • DE 601 29 392 12 also discloses a reciprocating engine with variable
  • Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the dependent claims.
  • Such a reciprocating engine comprises a crankshaft with at least one
  • the reciprocating engine comprises at least one adjusting device, by means of which the lever element for adjusting the
  • Rotary positions relative to the crank pin is adjustable, wherein the lever element is articulated on the one hand with the connecting rod and on the other hand with the actuating device.
  • the lever element can be adjusted by an at least substantially translatory movement of the adjusting device between the at least two rotational positions and that the actuating device at least indirectly a crankcase of the reciprocating engine is pivotally supported about a pivot axis.
  • the reciprocating piston engine according to the invention thus enables the representation of a very efficient operation as a result of a needs-based adaptation of the
  • Compression ratio of a corresponding cylinder of the reciprocating engine is adjustable, regardless of the possible adjustability and the setting of the compression ratio of at least one other such and to another crank pin and lever member of the reciprocating engine corresponding cylinder. This implies the realization of a so-called cylinder-selective adjustment of the compression ratio of the reciprocating engine, which improves the efficient operation of the same to another.
  • Tolerances can also be compensated in a cylinder-selective way. A classification of individual parts is not necessary. This is particularly advantageous in comparison to reciprocating engines, in which a simultaneous and dependent adjustment of
  • Lever element is actuated directly from the actuator. Additional space expenditure, for example, for an eccentric shaft to be rotated, which is connected via a lever to the lever element, is not necessary. This also keeps the weight and the number of parts of the reciprocating piston engine according to the invention low, which on the one hand the efficient operation and thus the low fuel consumption and on the other hand low cost is beneficial.
  • the adjusting device is in particular hingedly connected to the lever element, wherein the adjusting device comprises, for example, a translational movement executable rod which is connected to the lever element.
  • the lever member is further hingedly connected to a connecting rod, which in turn is articulated to a corresponding piston which is slidably disposed in an already executed cylinder of the reciprocating engine.
  • the piston then drives the crankshaft of the reciprocating engine due to gas expansion by combustion of fuel and air in the cylinder via the connecting rod and the crankpin, thus translating a translational movement of the piston in the cylinder into a rotational movement of the crankshaft.
  • the piston always performs the same stroke, so he always the same distance from its bottom dead center to its top dead center.
  • the position of top dead center and bottom dead center in the cylinder can now be changed by the lever element. If the lever element is changed relative to the crank pin by means of the adjusting device between the at least two rotational positions, a larger final volume, which is also referred to as compression volume, prevails in the cylinder at the top dead center of the piston in one of the rotational positions, and in the cylinder at least two Rotary positions and vice versa.
  • Compression volume means a reduction of the compression ratio, while a reduction of the compression volume, an increase of the
  • the adjusting device is pivotally supported about a pivot axis at least indirectly on a crankcase of the reciprocating engine. This ensures a movement and thus a compensation of the adjusting device as a result of movements of the
  • Reciprocating engine and its components which can be transmitted via the executed arrangement on the actuator. Furthermore, thereby connected to the lever element actuating device can perform movements of the lever member as a result of the rotation of the crankshaft and thus due to movements of the crank pin.
  • the executed support of the adjusting device is realized for example via a fixed relative to the crankcase shaft or a bolt or the like, about which the adjusting device is pivotable relative thereto.
  • Lever element via a threaded spindle of the adjusting device is adjustable.
  • the threaded spindle is a rotational movement, such as that of an electric motor, convertible into a translational movement, whereby the lever element is actuated.
  • the threaded spindle which is present for example as a threaded rod, directly connected to the lever element articulated. This represents a particularly cost-effective embodiment.
  • this is a particularly precise adjustment of the compression ratio of
  • the accuracy of this setting can be determined by the choice of the pitch of the thread of the threaded spindle.
  • a high pitch means that a relatively large translational path can be displayed and moved back by a few degrees when the threaded spindle is rotated.
  • With a shallow pitch of the thread of the threaded spindle the threaded spindle lays on rotation of the same even by many degrees a small, translational distance. If a high pitch promotes rapid adjustment of the lever member, a shallow pitch will favor the accuracy of the adjustment.
  • the adjusting device is hydraulically actuated.
  • Such a hydraulic actuation has the advantage that high control forces can be achieved with low control forces, which results in high cylinder pressures
  • the adjusting device comprises, for example, a cylinder having a working space, in which a piston, which is axially displaceable relative to the cylinder and connected to a push rod, is arranged.
  • Lever element by means of the adjusting device both from one of the rotational positions in the other of the rotational position and in the reverse direction is fast, accurate and adjustable with high forces.
  • a control piston of the adjusting device is provided, by means of which a respective amount of working medium in the control chambers is adjustable.
  • the control piston for example, control edges, which can release from the working fluid, which is designed in particular as a lubricant, such as lubricating oil, the reciprocating engine to flow channels of the actuator and / or close, so that a corresponding amount of the working fluid flow into the respective control chambers allow. Accordingly, if the working fluid is directed into one of the control chambers, its volume increases while the volume of the other control chamber decreases.
  • pumps not required for the operation of the adjusting device or can be made very small in their dimensions and performance, which keeps the energy consumption of the reciprocating engine according to the invention and thus the fuel consumption low. So there is a quasi almost independent pumping of the working medium in or out of the control rooms instead of due to the applied alternating forces. Also, an operation of the stated threaded spindle with these alternating forces is possible, which goes along with all the advantages mentioned in this context. Alternatively or additionally, the threaded spindle can also be operated with an electric motor.
  • the executed control piston is, for example, rotationally and / or translatorily actuated, wherein a translational actuation allows a simple and thus cost-effective design of the control piston and the space requirement of
  • the translational actuation of the control piston takes place, for example, via a rotationally fixed relative to the pivot axis of the actuator actuation element, for example, a pin penetrates the executed shaft or the executed bolt and obliquely, in particular transversely to the pivot axis by means of an actuator, for example, magnetically actuated.
  • the actuating element pushes the control piston in one direction, while a movement of the control piston in the direction opposite this direction is realized, for example, as a result of a force applied by a spring element, on the one hand on the piston and on the other hand on the adjusting device, in particular on the push rod
  • Actuator is supported. An integration of the control piston in the push rod, wherein the control piston at least partially in the push rod
  • Actuate and the control piston cooperate via an at least substantially arcuate surface, wherein the center of the arcuate surface is, for example, at least substantially on the pivot axis.
  • Compression ratio advantageously keeps constant. This has a particularly positive effect on the efficient operation of the reciprocating engine.
  • Another advantage of the control piston is that to set the desired
  • Compression ratio only a target position of the control piston, for example via the running actuator, to specify, whereby the corresponding channels are released or closed by the control edge.
  • the invention also includes a reciprocating engine with a crankshaft with at least one crankpin, on which a connected to a corresponding connecting rod lever element is mounted and with an adjusting device, by means of which
  • Lever element for adjusting the compression ratio of the reciprocating engine between at least two rotational positions is adjustable relative to the crank pin.
  • the crankshaft in this case has a plurality of crankpins, on each of which a lever element connected to a corresponding connecting rod is mounted, the lever elements each having an adjusting device is assigned by means of which the respective lever element independent of at least one other of the lever elements for adjusting the compression ratio of the reciprocating engine between at least two rotational positions relative to the respective crank pin is adjustable and that the adjusting devices are at least indirectly pivotally supported on a crankcase of the reciprocating engine about a pivot axis.
  • Advantageous embodiments of the first aspect of the invention are to be regarded as advantageous embodiments of the second aspect of the invention and vice versa.
  • the reciprocating engine of the second aspect of the invention thus allows adjustment of a respective, corresponding to a respective crank pin compression ratio of the reciprocating engine and Although independent of the setting of at least one further, corresponding to a further crank pin compression ratio.
  • two different compression ratios are adjustable. This is the one in this
  • Reciprocating engine with a very low fuel consumption and low C0 2 emissions results.
  • FIG. 1 is a perspective and partially sectioned view of a crank mechanism of a reciprocating engine with a crankshaft with four crank pins, on each of which a connected with a corresponding connecting rod lever member is mounted, each of the lever elements is assigned a hydraulically actuated and a translational movement executable actuator, by means of which the respective lever element for adjusting the compression ratio of the reciprocating engine between at least two rotational positions relative to the respective
  • Crank pin is adjustable
  • Fig. 2 is a perspective and partially sectioned view of a with a
  • FIG. 3 is another perspective view of the conrod and the
  • Fig. 4 is a partially sectioned plan view of the conrod and the
  • Fig. 5 is a sectional view of an adjusting device according to the preceding
  • FIG. 6 shows five longitudinal sectional views of the adjusting device according to FIG. 5 in FIG.
  • the crankshaft 12 has four crank pins 14, on each of which a lever element 16 is mounted, so that the lever elements 16 can rotate relative to the respective crank pins 14.
  • the lever elements 16 are each pivotally connected to a connecting rod 18 and designed as a transverse lever, which extend transversely to the axis of rotation of the crankshaft 12.
  • the connecting rods 18 in turn each have a connecting rod 22, via which the respective connecting rod 22 with a piston of the reciprocating piston displaceably arranged in a cylinder of the reciprocating engine is connectable.
  • the pistons of the reciprocating engine due to gas expansions by combustion of a fuel-air mixture in the respective cylinder through translational movements, which transmitted via the connecting rods 18 and the lever members 16 on the crank pin 14 and on to the crankshaft 12 and in a rotational movement of the crankshaft 12 are converted, so that the crankshaft 12 according to a direction arrow 20 rotates about its axis of rotation.
  • each actuating element 24 is associated with each lever element 16, which is connected in an articulated manner to the respective lever element 16.
  • the lever elements 16 By means of the adjusting devices 24, the lever elements 16 between at least two rotational positions relative to the respective Hubzapfen 14 rotatable about this. This causes an adjustment of a final volume, which is also referred to as compression volume, in the respective cylinder at top dead center of the respective piston, since the rotational position of the lever elements 16 relative to the respective crank pin 14 affects the translational position of the bottom and top dead center of the piston in the cylinder ,
  • a final volume which is also referred to as compression volume
  • Compression volume leads to a reduction of the compression ratio and / or vice versa.
  • the adjusting devices 24 perform a translational movement, which causes a rotation of the respective lever member 16 relative to the respective crank pin 14 about this.
  • the function of the actuators 24 is based on a
  • FIGS. 2 to 5 show the adjusting device 24, which has a working space 26
  • Hydraulic cylinder 28 includes. In the hydraulic cylinder 28 and its working space 26, a displaceable piston 30 is arranged, which is fixedly connected to a push rod 32.
  • the piston 30 divides the working space 28 into a first, in the Fig. 2 upper control chamber 34 and a lower, in Fig. 2, the second control chamber 36, wherein the control chambers 34 and 36 have a respective volume, which with a working medium in the form of Lubricating oil of the reciprocating engine can be acted upon.
  • the piston 30 and thus the push rod 32 is in a first end position in which the volume of the control chamber 34 is minimal and the volume of the control chamber 36 is maximum. In this case, the volume of the control chamber 36 is filled with the lubricating oil, while the control chamber 34 at least almost no
  • the lever element 16 assumes a first rotational position relative to the crank pin 14, in which a low compression ratio of, for example, ⁇ -7 is present. If the compression ratio is increased, the piston 30 and thus the
  • Adjusting device 24 moved out of the first end position shown in FIG. 2 and the piston 30 are moved in the direction of a surface 38.
  • the lubricating oil has to be removed from the control chamber 36 and lubricating oil introduced into the control chamber 34.
  • channels 40, 42, 44 and 46 are provided through which the lubricating oil can flow.
  • the channels 40, 42 and 44 are releasable and closable by corresponding control edges 48, 50 and 52 of a partially received in the push rod 32 control piston 54.
  • Flow control chamber 34 which lubricating oil via a shaft 62 can be fed.
  • the channel 46 is connected to a lubricating oil supply of the reciprocating engine and ensures the supply of the adjusting device 24 with sufficient working fluid in the form of lubricating oil.
  • Corresponding control valves in the form of check valves 56, 58 and 60 prevent an undesirable flow of lubricating oil.
  • the adjusting device 24 can in particular by using the check valves 56, 58 and 60 additional means for pressure enhancement of the lubricant, ie
  • Control chambers 34 and / or 36 pumps are controlled by Control chambers 34 and / or 36 pumps.
  • the adjusting device 24 performs a translational movement, it has the further advantage that it has only a small space requirement while achieving a very precise adjustment of the compression ratio, whereby the Reciprocating can be adapted very precisely to different operating points and thus enables a very efficient operation.
  • crank mechanism 10 and thus the reciprocating engine further have the advantage that the lever elements 16 can be adjusted independently of one another by the adjusting devices 24, as a result of which
  • Compression ratio of each cylinder is selectively adjustable.
  • the adjusting device 24 perform movements of the lever member 16 and movements of the reciprocating engine with and possibly compensate, it is pivotally held about the rotatably supported on a crankcase of the reciprocating engine shaft 62 and thus pivotally and indirectly supported on the crankcase.
  • the shaft 62 is fixed inter alia by fasteners 80.
  • Fig. 3 illustrates the operation of the control piston 54 for adjusting the
  • the adjusting device 24 comprises a pin 64 which penetrates the rotatably fixed to the crankcase shaft 62 and is connected to a substantially U-shaped actuating member 66.
  • the shaft 62 penetrating through a corresponding bore 64 and the substantially U-shaped actuating element 66 are integrally formed with each other and by means of an actuator, not shown, magnetically translatable in the direction of movement of the push rod 32 movable. If the actuator 66 via the pin 64 in
  • Control piston 54 against a spring force of a hand on the control piston 54 and on the other hand on the push rod 32 supported spring element 68 in the
  • Control chambers 34 and / or 36 can flow in or out.
  • a reverse operation of the control piston 54 is effected, for example, in that the actuating element 66 and the pin 64 are switched powerless, whereby the spring element 68 can push the control piston 54 in the direction of the actuating element 66, whereupon the actuating element 66 and the pin 64 of the push rod 32nd move away.
  • the control edges 48, 50 and 52, the channels 40, 42 and 44 free and the push rod 32 moves in the same direction in the other direction.
  • Compression ratio of the reciprocating engine only a specification of a desired position of the control piston 54 must be done via a specification of a desired position of the actuating element 66 and the pin 64 and the adjusting device 24 then adjusts automatically until the flow of the lubricating oil is interrupted. An additional operation of the control piston 54 to terminate the adjustment of the actuator 24 is not required. Furthermore, this means that any leaks due to wear, as it can occur over a very long lifetime, is quasi self-compensated by the adjusting device 24. It is merely an adaptation of the specification of the desired position of the control piston 54 and the actuating element 66 and the pin 64 needed. If appropriate, this adaptation can take place via a simple comparison of predetermined desired values with actual values detected by means of detection devices. This ensures a very precise adjustment of the compression ratio over a very long service life of the reciprocating engine and thus the representation of a very efficient and fuel-efficient operation derselbigen.
  • the actuating element 66 and the control piston 54 are not firmly connected to each other but act via a
  • arcuate surface 70 of the actuating element 66 together.
  • the center of the arcuate surface is at least substantially on the pivot axis of the adjusting device 24, which coincides with the central axis of symmetry of the shaft 62.
  • the arcuate surface 70 ensures a constant stroke and thus a constant movement of the control piston 54 even during a movement or at a Pivoting the adjusting device 24 about its pivot axis, wherein the
  • Control piston 54 carries out this pivoting movement while the actuator 66 as described rotatably.
  • the control piston 54 has a rounded head which abuts the arcuate surface 70 and can slide along it with little friction.
  • the cylinder 28 has a slot in which the actuating element 66 is arranged.
  • the cylinder 28 comprises three parts 74, 76 and 78, the part 74 being connected to the part 76.
  • the part 78 is also connected to the part 76 and is partially received in the part 76 and limited on the one hand the working space 26th
  • Fig. 6 shows the adjusting device 24 in five different from each other
  • the adjusting device 24 is in the upper end positions shown in FIGS. 1 to 5, in which the lowest compression ratio is present, which is, for example, ⁇ -7.

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

Abstract

L'invention concerne un moteur à piston alternatif comportant un vilebrequin (12) pourvu d'au moins un maneton (14) sur lequel est monté un élément levier (16) relié à une bielle correspondante (18), et d'au moins un dispositif de réglage (24) qui permet de régler l'élément levier (16) pour le réglage du taux de compression du moteur à piston alternatif entre au moins deux positions de rotation par rapport au maneton (14). L'élément levier (16) peut être réglé par un mouvement au moins sensiblement de translation du dispositif de réglage (24) entre les deux positions de rotation ou plus.
PCT/EP2010/007364 2010-03-02 2010-12-03 Moteur à piston alternatif Ceased WO2011107131A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010009909.0 2010-03-02
DE201010009909 DE102010009909B3 (de) 2010-03-02 2010-03-02 Hubkolbenmaschine

Publications (1)

Publication Number Publication Date
WO2011107131A1 true WO2011107131A1 (fr) 2011-09-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/007364 Ceased WO2011107131A1 (fr) 2010-03-02 2010-12-03 Moteur à piston alternatif

Country Status (2)

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DE (1) DE102010009909B3 (fr)
WO (1) WO2011107131A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002012694A1 (fr) 2000-08-08 2002-02-14 Daimlerchrysler Ag Moteur a combustion interne a piston alternatif, a taux de compression variable
DE69804297T2 (de) 1997-05-09 2002-10-02 Vianney Rabhi Vorrichtung zum verstellen des hubvolumens und/oder des effektiven verdichtungsverhältnisses einer brennkraftmaschine während des betriebs
JP2003322036A (ja) * 2002-05-07 2003-11-14 Nissan Motor Co Ltd 内燃機関の可変圧縮比機構
EP1418322A2 (fr) * 2002-11-05 2004-05-12 Nissan Motor Co., Ltd. Système de taux de compression variable pour un moteur à combustion interne et méthode de commande du système
EP1520970A1 (fr) * 2003-10-02 2005-04-06 Peugeot Citroen Automobiles S.A. Actionneur hydraulique pour moteur à combustion interne et moteur à combustion interne comportant au moins un tel actionneur hydraulique
WO2007092168A2 (fr) 2006-02-02 2007-08-16 Edward Charles Mendler Capteur de pression de combustion
DE60129392T2 (de) 2000-10-12 2007-10-31 Nissan Motor Co., Ltd., Yokohama Mechanismus für das variable Verdichtungsverhältnis einer Brennkraftmaschine
JP2008115830A (ja) * 2006-11-08 2008-05-22 Nissan Motor Co Ltd レシプロ式内燃機関の制御装置及び制御方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE575230C (de) * 1930-07-05 1933-04-26 Otto Severin Ruud Brennkraftmaschine mit durch Verlegung des Kolbenhubes sich selbsttaetig der Belastung anpassendem veraenderlichen Verdichtungsraum
DE102006003737B3 (de) * 2006-01-24 2007-06-06 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Hubkolben-Verbrennungsmotor

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69804297T2 (de) 1997-05-09 2002-10-02 Vianney Rabhi Vorrichtung zum verstellen des hubvolumens und/oder des effektiven verdichtungsverhältnisses einer brennkraftmaschine während des betriebs
WO2002012694A1 (fr) 2000-08-08 2002-02-14 Daimlerchrysler Ag Moteur a combustion interne a piston alternatif, a taux de compression variable
DE60129392T2 (de) 2000-10-12 2007-10-31 Nissan Motor Co., Ltd., Yokohama Mechanismus für das variable Verdichtungsverhältnis einer Brennkraftmaschine
JP2003322036A (ja) * 2002-05-07 2003-11-14 Nissan Motor Co Ltd 内燃機関の可変圧縮比機構
EP1418322A2 (fr) * 2002-11-05 2004-05-12 Nissan Motor Co., Ltd. Système de taux de compression variable pour un moteur à combustion interne et méthode de commande du système
EP1520970A1 (fr) * 2003-10-02 2005-04-06 Peugeot Citroen Automobiles S.A. Actionneur hydraulique pour moteur à combustion interne et moteur à combustion interne comportant au moins un tel actionneur hydraulique
WO2007092168A2 (fr) 2006-02-02 2007-08-16 Edward Charles Mendler Capteur de pression de combustion
JP2008115830A (ja) * 2006-11-08 2008-05-22 Nissan Motor Co Ltd レシプロ式内燃機関の制御装置及び制御方法

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