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WO2012013264A1 - Procédé pour faire fonctionner un moteur à piston alternatif - Google Patents

Procédé pour faire fonctionner un moteur à piston alternatif Download PDF

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Publication number
WO2012013264A1
WO2012013264A1 PCT/EP2011/002892 EP2011002892W WO2012013264A1 WO 2012013264 A1 WO2012013264 A1 WO 2012013264A1 EP 2011002892 W EP2011002892 W EP 2011002892W WO 2012013264 A1 WO2012013264 A1 WO 2012013264A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression ratio
engine
reciprocating engine
cylinder
reciprocating
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/EP2011/002892
Other languages
German (de)
English (en)
Inventor
Marc Wodischek
Simone NOWAK
Bernd-Heinrich Schmitfranz
Tilmann RÖMHELD
Michael Wagenplast
Dieter Nowak
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 WO2012013264A1 publication Critical patent/WO2012013264A1/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/04—Introducing corrections for particular operating conditions
    • F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
    • F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
    • F02D41/065—Introducing corrections for particular operating conditions for engine starting or warming up for starting at hot start or restart
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N11/00—Starting of engines by means of electric motors
    • F02N11/08—Circuits specially adapted for starting of engines
    • F02N11/0814—Circuits specially adapted for starting of engines comprising means for controlling automatic idle-start-stop
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N99/00—Subject matter not provided for in the other groups of this subclass
    • F02N99/002—Starting combustion engines by ignition means
    • F02N99/006—Providing a combustible mixture inside the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/04—Introducing corrections for particular operating conditions
    • F02D41/042—Introducing corrections for particular operating conditions for stopping the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N19/00—Starting aids for combustion engines, not otherwise provided for
    • F02N19/004—Aiding engine start by using decompression means or variable valve actuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N2300/00—Control related aspects of engine starting
    • F02N2300/20—Control related aspects of engine starting characterised by the control method
    • F02N2300/2002—Control related aspects of engine starting characterised by the control method using different starting modes, methods, or actuators depending on circumstances, e.g. engine temperature or component wear
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Definitions

  • the invention relates to a method for operating a reciprocating piston engine according to claims 1 and 5.
  • DE 199 55 250 A1 discloses a method for monitoring the function of a
  • a change in the engine operating parameter is an indication of a correct function of the device for the variable adjustment of the cylinder compression.
  • one or more criteria for a difficult starting the machine are checked. If at least one criterion for a difficult starting is met, then the cylinder compression in at least one cylinder is reduced to a predetermined minimum value until the engine speed has been increased to a defined threshold, in which case the cylinder compression is increased.
  • EP 1 431 559 A2 shows an air intake control device for an engine having a mechanism for variably adjusting an amount of intake air which variably controls an amount of fresh air flowing into the engine and a motor
  • Mechanism for variably setting a compression ratio which includes Compression ratio of the engine variable controls. Sensors record operating conditions of the engine as well as the compression ratio. Further, a control device is provided, which is designed with the sensors, the mechanism for variably adjusting the amount of intake air and with the mechanism for variable
  • Adjustment of the compression ratio to be connected to control the mechanism for the variable adjustment of the amount of intake air based on the compression ratio and on the operating conditions of the engine.
  • Compression ratio of an internal combustion engine with a mechanism for changing the compression ratio of the internal combustion engine, at least between a first higher and a second lower stage, corresponding to
  • the Machine operating conditions and with a compression ratio measuring device for determining the current compression ratio.
  • the device contains a
  • Compression ratio measuring device and a protective device for changing and maintaining the compression ratio at the lower level, when the
  • Compression ratio measuring device detects.
  • map-controlled, variable compression ratio which at least one
  • Load detection, a load request detection and an actuator for adjusting the compression ratio comprises. Further, a motor controller is provided, which is in communication with a time signal generator, wherein the engine control for the
  • Determining the variable compression ratio to be set in an area of the internal combustion engine has signal lines for detecting at least part of the engine load.
  • the internal combustion engine further comprises a in the
  • DE 102 58 872 A1 discloses a method for operating a multi-cylinder
  • a variable compression ratio internal combustion engine in which starting of the internal combustion engine is performed at a compression ratio that is opposite
  • Compression ratios is reduced during normal operation of the internal combustion engine.
  • Reciprocating engines have potential to reduce the energy consumption of the reciprocating engine.
  • the first aspect of the invention relates to a method for operating a
  • Reciprocating engine in particular for a motor vehicle, in which a
  • the reciprocating piston engine which is in a deactivated operating state, is activated with a set compression ratio, which is opposite a preceding one, in particular directly
  • Quick start function means that fuel is introduced into the cylinder and in particular directly injected and ignited, wherein the high compression ratio starting enables the generation of a high force for starting and thus the starting process of the reciprocating engine can be completed very quickly. This is especially in a so-called start / stop operation of
  • Reciprocating engine automatically deactivated, for example, when stopping the motor vehicle at a traffic light and automatically activated again when starting or immediately before starting.
  • the described quick start function in particular by starting with the increased compression ratio allows a particularly fast starting of the deactivated internal combustion engine, whereby a
  • the reciprocating engine for example, with respect to the subsequent startup, i. opposite to the subsequent activation of the
  • the reciprocating piston engine located in the activated operating state with this compression ratio is deactivated, in particular automatically deactivated during start / stop operation, then it may be advantageously provided that the compression ratio with which the reciprocating piston engine is activated in the deactivated operating state is activated, at the activation preceding the deactivation (when the traffic light is reached) the then in the activated operating state reciprocating engine is set.
  • a compression ratio which is higher than the previously activated operating state is set, which then also exists during the deactivated operating state following the activated operating state and during the subsequent start (activation).
  • the desired high or higher compression ratio when starting the internal combustion engine does not have to be set during the starting process, but already exists, since it has already been set in advance.
  • the starting process and in particular the quick start can be performed in a very short time and the reciprocating engine can be started very fast.
  • a realized by the adjustment of the compression ratio according to the invention when activating the reciprocating engine oxygen excess in the cylinder additionally ensures a rapid heating in the flow direction of an exhaust gas of the reciprocating engine, which is ejected from the cylinder through the piston, downstream of the reciprocating engine arranged catalyst so that this particular quickly reaches an advantageous operating temperature (light-off temperature) and can clean the exhaust gas.
  • the harmful emissions of the reciprocating engine can be kept very low and even in time very early after starting derselbigen.
  • the reciprocating engine preferably has a plurality, i. at least two cylinders, in each of which a piston is received translationally movable and which is associated with at least one adjusting device for adjusting the respective compression ratio of the cylinder.
  • This allows a cylinder-individual, variable, controlled or regulated, gradual or continuous adjustment of the respective compression ratios.
  • Cylinder-specific adjustment of the compression ratios means that each of the compression ratios set for themselves and thus the cylinder can be adjusted very precisely and as needed to the current operating point of the reciprocating engine.
  • the compression ratio of a cylinder can be set individually and independently of the other compression ratios of the other cylinder. So it is possible that at least two
  • Reciprocating engine can be operated with at least two different compression ratios. From the cylinder-specific setting of the
  • Reciprocating deactivated or activated with a set compression ratio which is at least temporarily set or can be set even in an activated operating state of the reciprocating engine.
  • Compression ratios during normal operation ie during the activated operating state of the internal combustion engine, can be adjusted and can be used to represent a very efficient operation of the reciprocating engine.
  • deactivation and / or activation
  • Reciprocating engine can be adjusted or adjusted. Rather, these can also be set during activated operating state, so that the range of compression ratios to be set is particularly large. Thus, a very high flexibility is created to adapt the reciprocating engine to a variety of different operating points to represent efficient operation.
  • Reciprocating engine is a separate starting device, in particular a starter, not required for activating the reciprocating engine or must not be used because the reciprocating engine can be activated by the quick start function as a result of the introduction of fuel into the cylinder and the ignition desselbigen without further starting device.
  • This keeps the weight of the motor vehicle in a small frame and helps to avoid or solve package problems, especially in a space-critical area such as an engine compartment of the motor vehicle. Nonetheless
  • the car such a starting device, in particular a starter includes, which is used when activating the reciprocating engine in the presence of certain conditions or can be to activate the reciprocating engine.
  • a further advantage of the activation of the reciprocating engine with the compression ratio increased compared to the previously activated operating state is that the oxygen surplus in the cylinder gives rapid heating of the cylinder, which is also referred to as the combustion chamber, and thus of the reciprocating engine.
  • the second aspect of the invention relates to a method for operating a
  • Reciprocating engine in particular for a motor vehicle, in which a
  • Compression ratio of at least one cylinder of the reciprocating engine, in which a piston is taken translationally guided, is adjusted by means of a corresponding actuator with the cylinder.
  • Compression ratio of the cylinder in operation reciprocating engine on the other hand, a different compression ratio is set, which in a subsequent to the deactivation, in particular directly
  • the second aspect of the invention allows a particularly good and needs-based and especially fast starting or activating the reciprocating engine out of its deactivated operating state, since the advantageous for activating the reciprocating engine in the presence of certain conditions compression ratio is already set in the previous deactivation or was and thus in the
  • Activation is present at least almost without delay.
  • the compression ratio does not have to be set when activating the reciprocating engine be, which would undesirably prolong the starting process, but the desired and adapted to a desired starting behavior of the reciprocating engine compression ratio is already present.
  • Reciprocating engine increased compared to the activated operating state
  • Another possible starting function is, for example, to start the reciprocating engine with a separate starting device, in particular a starter. Then it is particularly advantageous, a relation to the compression ratio of the in operation, ie in activated operating state, located reciprocating engine increased
  • Compression ratio keeps the force required to start the reciprocating engine low, so that the starter has to muster a small force the
  • the reciprocating piston engine comprises such a separate starting device, in particular a starter, then in the context of the first and the second aspects of the invention, depending on the type of start, for example by a driver's request
  • the reciprocating engine can be started either by means of the starting device or without the aid of the starting device and only by injecting and igniting fuel in the cylinder.
  • the methods according to the invention enable a fast, at least almost delay-free, comfortable and therefore very good start and stop behavior of the reciprocating piston engine, and a particularly efficient behavior of the same during activation or deactivation.
  • Fig. 1 a detail of a schematic side view of a crank mechanism for a reciprocating engine with a plurality of cylinders and the cylinders associated pistons, wherein by means of the crank mechanism respective compression ratios of the cylinder cylinder individually independently adjustable;
  • Fig. 2 shows a detail of a schematic side view of the crank mechanism according to
  • FIG. 1 with a schematic diagram for detecting a position of a
  • Compression ratio wherein based on the detected position of the control piston, the set compression ratio of the corresponding cylinder is determined.
  • Fig. 1 shows a crank mechanism 10 for a reciprocating engine of a motor vehicle, wherein the reciprocating piston engine comprises a plurality of cylinders.
  • the crank mechanism 10 will be described with reference to FIG. 1 with respect to one of these cylinders corresponding to the crank mechanism 10 of the reciprocating piston engine. It is understood that the description of the crank mechanism 10 and the cylinder is analogous to the other cylinders of the reciprocating piston engine, in particular all others.
  • the crank mechanism 10 comprises a crankshaft 12, which has main bearing points, via which the crankshaft 12 is mounted in a crankcase of the reciprocating engine. Furthermore, the crankshaft 12 crank webs, of which such a crank arm 14 is shown in FIG. 1. In addition, the crankshaft 12 crank pin, of which a crank pin 16 is shown in FIG. The crankpin 16 corresponds to a cylinder of the reciprocating engine. In the same way, the other crank pin correspond respectively to a cylinder of
  • crank operation 10 includes a transverse lever 18, which is a first
  • Lever element 20 and a second lever element 22 includes, which are connected to each other, for example, screwed together, are.
  • the transverse lever 18 is rotatably mounted on the crank pin 16 relative to this about an axis of rotation 25 and performs strokes in a rotation of the crankshaft 12, for example, during operation of the reciprocating engine, with out.
  • the transverse lever 18 has a first bearing 24, on which a connecting rod 26 of the crank mechanism 10 is articulated.
  • the connecting rod 26 can rotate about a rotation axis 28.
  • the axis of rotation 28 is spaced from the axis of rotation 25 in the radial direction of the crank pin 16 by a first lever arm n.
  • the crank mechanism 10 also includes a piston 30, which corresponds to the cylinder, to which the crank pin 16 corresponds, and in which the piston 30 is received translationally movable.
  • the piston 30 is pivotally connected to the connecting rod 26 via a further bearing 32. Attached is the piston 30 to the connecting rod 26 via a piston pin, which in the piston 30 by a corresponding
  • Circlip is secured in the axial direction of the piston pin. If the piston 30 is moved translationally in the cylinder as a result of combustion processes, this translational movement is converted via the connecting rod 26, the transverse lever 18 and the crankpin 16 into a rotational movement of the crankshaft 12.
  • the transverse lever 18 has a further bearing 34, on which a control piston 36 of an adjusting device 38 of the reciprocating engine articulated and with the
  • Cross lever 18 is connected.
  • the control piston 36 can rotate about an axis of rotation 40 of the bearing 34.
  • the axis of rotation 40 is spaced by a further lever h 2 in the radial direction of the crank pin 16 of the rotation axis 25. It can be seen that the levers and h 2 differ in terms of amount.
  • the lever h 2 is larger than the lever h ⁇ . It is equally possible that the lever and h 2 are equal in magnitude, or the lever h is greater than the lever H 2.
  • Control piston 36, the adjusting device 38 comprises a housing 41 through which a cylinder is formed. In the cylinder, the control piston 36 is held translationally guided guided. By supplying or removing a working medium into the cylinder, For example, compressed air, hydraulic fluid or the like, the control piston 36 can be moved translationally in accordance with a direction arrow 43 and with respect to the housing 41 according to a direction arrow 44 extended or retracted according to a direction arrow 46. In contrast to such an active attitude is also a passive one
  • control piston 36 is moved as a result of gas and inertial forces of the reciprocating engine, which act on the piston 30 on the control piston 36.
  • the control piston 36 is released by the working fluid and valve means, for example check valves which are connected via other control valves, for example, a control slide with control edges which lines for the working fluid release or obstruct, in a desired direction of movement and opposite in the desired direction of movement
  • Movement direction blocked or completely held It is a kind of hydraulic freewheel.
  • This embodiment has the advantage that a desired compression ratio can be set without and with only a very small additional energy input. It is also possible to actuate the control piston 36 by means of an electromagnet.
  • crank pin 16 moves up and down, which also leads to a movement of the transverse lever 18.
  • the adjusting device 38 also moves by the housing 41 pivotable about a pivot axis 42 at a
  • control piston 36 If the control piston 36 is moved translationally according to the directional arrow 43, this leads to a rotation of the transverse lever 18 relative to the crank pin 16 according to a directional arrow 48, whereby the compression ratio of the corresponding cylinder can be adjusted.
  • the adjustment of the control piston 36 acts on the ratio of the lever and h 2 to the same extent, reinforced or reduced.
  • the adjustment of the control piston 36 leads to an adjustment or adjustment of the top dead center of the piston 30 in the cylinder and thus to an adjustment or adjustment of the compression volume v c of the corresponding cylinder.
  • the adjustment of the control piston 36 also affects the stroke and thus the stroke volume v H of the piston 30.
  • the stroke volume v H reduces as the flow increases
  • each of the cylinders of the reciprocating engine associated with such a control device 38 by means of which the compression ratio of the corresponding cylinder can be adjusted independently of the other cylinders.
  • This cylinder-specific adjustment of the corresponding compression ratios allows a very precise and extremely needs-based adjustment of
  • Compression ratio can be used to adjust this variable, continuously or stepwise.
  • FIG. 2 A schematically illustrated in FIG. 2 sensor 50 detects the position of the control piston 36 and a
  • Control rod this relative to a reference point and / or the stroke of the control piston 36 and a position and / or the stroke characterizing signal.
  • This signal is transmitted according to a directional arrow 52 to a position control 54 of a control device 56, wherein the control device 56 is formed, for example, as a control unit of the reciprocating engine.
  • the control device 56 further comprises a combustion control 58, by means of which the combustion processes in the cylinders of the reciprocating engine are controlled or regulated.
  • Combustion control 58 inter alia, a feedback 60 of the set actual compression ratio, which is determined by the position control 54 based on the signal detected by the sensor 50 and thus based on the position of the control piston 36.
  • a feedback 60 of the set actual compression ratio which is determined by the position control 54 based on the signal detected by the sensor 50 and thus based on the position of the control piston 36.
  • Combustion control 58 a preset 62 of a target compression ratio to the position control 54, the target compression ratio in a position to be set of the control piston 36 transferred.
  • the position control 54 also takes into account any other system variables 64 of the crank mechanism 10 and the
  • the determined position for setting the desired compression ratio or a position of the control piston 36 characterizing signal is transmitted to a control 65 for the control device 38, which transmits corresponding control signals to an actuator 66, by means of which the control piston 36 moves and thus the
  • Compression ratio is set.
  • FIG. 3 shows a possibility of detecting the or at least one position of the control piston 36.
  • the sensor 50 is designed as a Hall sensor with a detection part 68 which cooperates with an arcuate bipolar encoder plate 70 of the Hall sensor.
  • the detection part 68 is, for example, fixed to the Hall sensor.
  • Control piston 36 allows. Also, the magnetic field of the encoder plate 70 is
  • the control piston 36 is designed, for example, as a hydraulic piston and can be actuated such that the cylinder, with which the cylinder formed by the housing 41 is acted upon by hydraulic fluid, ie the hydraulic fluid is supplied to the housing or removed.
  • the supply of hydraulic fluid into the cylinder or out of the cylinder can be controlled or regulated, for example via an electromagnet, which has particularly fast switching times, so that the
  • Reciprocating engine can be adjusted.
  • control piston 36 is designed as an electromagnet or at least partially as part of such an electromagnet, so that the
  • Control piston 36 can be compacted very quickly to set the compression ratio. Furthermore, it is possible that the control piston 36 is designed as a pneumatic piston and is actuated by supply or discharge of compressed air in or out of the cylinder. The supply or discharge of compressed air can also be controlled or controlled by an electromagnet, which has particularly short switching times and allows the fast operation of the control piston 36.
  • control piston 36 is actuated by means of a gear, in particular a pinion, the control piston 36 is at least partially formed as a rack with a toothing for actuating the control piston 36 with a corresponding toothing of the gear, in particular the Ritzels, cooperates.
  • control piston 36 is actuated by means of a cam, wherein the control piston 36 is at least partially formed as a rod, which with the cam for actuating the control piston 36th
  • control piston 36 can at least partially be designed as a spindle and be actuated by means of a ball screw to set the

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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 procédé pour faire fonctionner un moteur à piston alternatif, en particulier pour un véhicule à moteur, selon lequel un taux de compression d'au moins un cylindre du moteur à piston alternatif, dans lequel un piston (30) est logé en étant guidé de manière à effectuer des mouvements de translation, est ajusté au moyen d'un dispositif de réglage (38) correspondant au cylindre, le moteur à piston alternatif se trouvant dans un état de fonctionnement désactivé étant activé avec un taux de compression ajusté, augmenté par rapport à un taux de compression ajusté dans un état de fonctionnement activé antérieur. L'invention se caractérise également en ce que lors d'une activation du moteur à piston alternatif en service, avec un taux de compression établi du cylindre, un taux de compression comparativement différent est établi, ledit taux de compression étant au moins sensiblement maintenu en cas d'activation du moteur à piston alternatif, faisant suite à la désactivation.
PCT/EP2011/002892 2010-07-28 2011-06-11 Procédé pour faire fonctionner un moteur à piston alternatif Ceased WO2012013264A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010032488.4 2010-07-28
DE102010032488A DE102010032488A1 (de) 2010-07-28 2010-07-28 Verfahren zum Betreiben einer Hubkolbenmaschine

Publications (1)

Publication Number Publication Date
WO2012013264A1 true WO2012013264A1 (fr) 2012-02-02

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Application Number Title Priority Date Filing Date
PCT/EP2011/002892 Ceased WO2012013264A1 (fr) 2010-07-28 2011-06-11 Procédé pour faire fonctionner un moteur à piston alternatif

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DE (1) DE102010032488A1 (fr)
WO (1) WO2012013264A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013003682B4 (de) 2013-02-27 2018-03-15 Victor Gheorghiu Verfahren zur Laststeuerung und Zylinderabschaltung einer Brennkraftmaschine arbeitend nach dem realen Viertakt-Atkinson-Zyklus
WO2016016197A1 (fr) * 2014-07-29 2016-02-04 Fev Gmbh Procédé pour faire fonctionner un moteur à combustion interne présentant un taux de compression de redémarrage réglable
CN113227560B (zh) * 2018-11-06 2023-08-01 日产自动车株式会社 内燃机的控制方法及控制装置

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DE3825369C1 (fr) 1987-07-30 1989-05-03 Toyota Jidosha K.K., Toyota, Aichi, Jp
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