EP2550439B1 - Moteur a combustion interne - Google Patents

Moteur a combustion interne Download PDF

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Publication number
EP2550439B1
EP2550439B1 EP11718894.6A EP11718894A EP2550439B1 EP 2550439 B1 EP2550439 B1 EP 2550439B1 EP 11718894 A EP11718894 A EP 11718894A EP 2550439 B1 EP2550439 B1 EP 2550439B1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
sub
unit
rotation
internal combustion
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.)
Not-in-force
Application number
EP11718894.6A
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German (de)
English (en)
Other versions
EP2550439A1 (fr
Inventor
Oswald Friedmann
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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.)
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Publication of EP2550439A1 publication Critical patent/EP2550439A1/fr
Application granted granted Critical
Publication of EP2550439B1 publication Critical patent/EP2550439B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D25/00—Controlling two or more co-operating engines
    • F02D25/04—Controlling two or more co-operating engines by cutting-out engines
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2186—Gear casings

Definitions

  • the invention relates to an internal combustion engine comprising a plurality of subunits each having a crankshaft part, on each of which at least one piston is received by means of a connecting rod on a crank of the crankshaft part, wherein at least a first subunit permanently operated during operation of the internal combustion engine and at least one further subunit is switched off ,
  • Internal combustion engines convert chemically into kinetic energy by combustion of energy stored in the fuel by moving pistons, which are received in a reciprocating internal combustion engine on a crankshaft by means of connecting rods, up and down in accordance with the two- or four-stroke principle while rotating the crankshaft in the cylinders.
  • internal combustion engines must have a wide power range to cover the power requirements of various modes such as city driving, overland and highway driving. Most internal combustion engines are oversized for an average power requirement and are therefore operated at a degraded efficiency that results in increased fuel demand.
  • a reciprocating internal combustion engine which is divided into two subunits, each containing a part of the working cylinder of the internal combustion engine, the connecting rod and piston are connected to a crankshaft part.
  • the crankshaft parts of the two subunits can be coupled to one another by means of a clutch, so that under full load and closed clutch both subunits are combined and in the part load range a subunit is decoupled by opening the clutch.
  • the decoupling takes place by means of an axial displacement of the decoupled subunit, wherein the crankshaft part and the connecting rod on the crankshaft cranks must be stored in axial movable bearings.
  • connection and disconnection of the two subunits of the internal combustion engine is achieved by means of a device for axial displacement, which must be operated at full load with additional energy, which in turn degrades the efficiency of the internal combustion engine.
  • the object of the invention is to improve the efficiency of internal combustion engines, in particular with a plurality of separable subunits.
  • an internal combustion engine comprising a plurality of subunits each having a crankshaft part, on each of which at least one piston is received by means of a connecting rod on a crank of the crankshaft part, wherein at least a first subunit permanently operated during operation of the internal combustion engine and at least one more Subunit is switched off, the crankshaft parts of the at least one first subunit and an adjacent, disconnectable second subunit are rotationally connected to each other and with respect to their axes of rotation are mutually displaceable such that a registered from the crankshaft part of the first subunit in the crankshaft part of the second subunit rotational movement substantially canceled becomes.
  • the rotationally locked connection between two adjacent subunits during the separation of the two subunits by parallel displacement whose Kurbelellwellenmaschine obtained against each other. Due to the parallel displacement, the strokes of the pistons, which are predetermined by the cranks of the crankshaft parts of the two subunits relative to each other so relativized, so that the strokes of the pistons of abraceden subunit decrease with increasing distance of the axes of rotation of the crankshaft parts from each other and at a predetermined distance of a crankshaft part from the other, which is substantially equal to a distance of the axes of rotation of the cranks of the crankshaft parts from their axes of rotation, to zero.
  • the axially fixed mounting of the two crankshaft parts can be maintained in their housing-fixed recordings and the connecting rods remain axially fixed to the cranks.
  • the subunits may be part of an internal combustion engine in a series or V-shaped arrangement of the cylinders. In an arrangement of the cylinder in V-shape, two connecting rods may be provided on a crank of the crankshaft parts.
  • the internal combustion engine may be designed according to the diesel or petrol principle and have gas exchange via camshafts or individually controlled valves.
  • a single housing of the internal combustion engine is provided, in which one or more subunits with pistons, connecting rods and crankshaft parts firmly housed and one or more subunits are housed on a limited relative to the housing displaceably arranged carriages.
  • crankshaft part with the connecting rods and pistons of a subunit can be mounted axially fixed on the carriage, which in turn is axially displaceably guided axially fixed and substantially perpendicular to the axis of rotation of the crankshaft part of the permanently driven subunit.
  • the parallel displacement of one of the two subunits relative to the other, preferably the disconnectable subunit relative to the permanently operated subunit is effected by means of an actuator, for example a hydrodynamic, hydrostatic, electrical or from this combined actuator.
  • an actuator for example a hydrodynamic, hydrostatic, electrical or from this combined actuator.
  • an eccentric arm which can be extended depending on the displacement of the crankshaft parts can be provided.
  • the eccentric arm is fixed to one of the crankshaft parts and rotatable on the other, for example by means of a journal.
  • Such a journal can in the be included slidably or roller bearings associated crankshaft part.
  • the compensated during the displacement as parallel displacement of the two crankshaft parts difference in length is compensated according to the inventive idea by means of a linear guide in Exzenterarm.
  • This may be a rolling or sliding bearing linear guide, which can transmit force in the circumferential direction and is at least secured against loss in the axial direction.
  • a so-called dovetail guide has proven to be advantageous in the case of a plain bearing.
  • the eccentric arm is displaced on one of the crankshaft parts on its axis of rotation and on the other crankshaft part substantially at a distance corresponding to a distance between the axis of rotation of the crankshaft part and an axis of rotation of the crankshaft cranking distance from the axis of rotation of the crankshaft part and fixed to one of the crankshaft parts and to the other crankshaft part rotatably arranged.
  • an advantageous embodiment of an internal combustion engine to a permanently operated subunit having a fixedly mounted relative to a housing crankshaft part wherein the crankshaft part of the turn-off subunit parallel to the axis of rotation of the crankshaft part of the permanently operated subunit (parallel) is displaced, not displaceable crankshaft part receives the Exzenterarm and the displaceable crankshaft part by means of a provided on the Exzenterarm, rotationally displaceable to the axis of rotation of the displaceable crankshaft part by an offset and depending on a displacement of the displaceable crankshaft part radially over the axis of rotation of the non-displaceable crankshaft part movable bearing journal with the non-displaceable crankshaft part rotationally connected is.
  • the eccentric arm In order to utilize the Coriolis force when coupling the uncoupled subunit, the eccentric arm, with the subunit switched off, has a center of gravity outside the axis of rotation of its crankshaft part.
  • the radially outer mass part of the eccentric arm experiences a rotational acceleration in the sense of a pirouette, as a result of the incipient rotation of the crankshaft part of the coupling crankshaft part, so that this is due to the decreasing radius the mass part formed moment of the parallel displacement is used and the displacement force is reduced as Aktorkraft.
  • an axial clamping of the crankshaft parts of a permanently driven and a switched subunit be provided, so that they are braced axially against each other.
  • the bracing can be done, for example, by exerting axial pressure on the eccentric arm in the coaxial arrangement of the crankshaft parts, starting from a pressure force transmitted to a crankshaft part and displacing a hydraulic piston.
  • the subunits can be braced against each other axially backlash coupled unit.
  • the at least one crankshaft part of the decoupled subunit receiving carriage relative to a permanently operated subunit receiving housing are clamped axially free of play.
  • an operation results according to the following method: In coaxial with each other arranged crankshaft parts all connecting rods are arranged in line about an axis of rotation of the crankshaft of the internal combustion engine.
  • the uniform cranks of crankshaft parts dictate the double piston stroke of this.
  • the crankshaft parts are connected to each other by means of the eccentric arm, the dovetail guide is pushed together on a minimum balancing path, the bearing pin transmits the gas forces introduced via the connecting rods from the pistons into the crankshaft part of the connected subunit to the crankshaft part of the permanently operated subunit.
  • the crankshaft part of the disengageable subunit together with the bearing by means of the actuator is preferably displaced within half a crankshaft revolution into a position spaced from the axis of rotation of the crankshaft part of the permanently operated subunit, which is essentially at a distance of the axis of rotation of a crank to the axis of rotation of a crankshaft part equivalent.
  • the eccentric arm on his linear guide as dovetail joint is extended accordingly. Due to the kinematic conditions of the eccentric lever results in the set position of the disconnected subunit despite a rotational drive of the eccentric lever by the crankshaft part of the permanently operated subunit no rotation of the crankshaft part.
  • FIG. 1 shows the internal combustion engine 1 in a schematic oblique view with the subunits 2, 3, each with two arranged in series, by means of the connecting rods 4, 4a arranged on the crankshaft parts 5, 6 pistons 7, 7a.
  • the pistons 7, 7a are guided in a cylinder housing, not shown, along a predetermined by the cranks 8 of the crankshaft parts 5, 6 piston stroke and form with this and a cylinder head also not shown with valves for controlling the gas exchange and optionally ignition the displacement of the internal combustion engine.
  • the two subunits 2, 3 are connected to one another by means of the two housing parts 9, 10, which may also be combined to form a common housing 11.
  • the subunit 2 is provided as a permanently operated subunit of the internal combustion engine, the is always operated during operation of the internal combustion engine 1, while the subunit 3 is designed to be switched off.
  • the crankshaft part 5 of the subunit 2 is fixedly mounted in the housing part 9 and thus firmly held about its axis of rotation 12 rotatable in the common housing 11.
  • the crankshaft part 6 of the subunit 3 with the axis of rotation 12 is mounted axially fixed on the carriage 14, which is displaceable relative to the housing part 10 and thus relative to the housing 11 parallel to the axis of rotation 12.
  • the carriage 14 is displaceable by the distance 18, which essentially corresponds to the distance 19 between the rotation axis 13 and the rotation axis 20 of the crank 8, by which the connecting rods 4 are rotatable about the offset 8.
  • the rotational closure connection 16 is effective, which is formed from the Exzenterarm 17 with a length compensation, which causes in the state shown here the coaxial arrangement of the axes of rotation 12, 13 of the crankshaft parts 5, 6, a rotational coupling of the two crankshaft parts, so in that the torque introduced into the crankshaft part 5 as a result of the combustion of fuel in the displacements and the following acceleration of the pistons 7a is transferred completely to the crankshaft part 5.
  • FIG. 2 shows the internal combustion engine 1 of FIG. 1 In the uncoupled state of the subunit 3 of the subunit 2.
  • the carriage 14 is moved to the stop 21 of the housing part 10, so that corresponding to the two axes of rotation 12, 13 of the crankshaft parts 5, 6 by the distance 19 (Fig. FIG. 1 ) and the axis of rotation 12 is substantially coaxial with the axis of rotation 22, which is substantially the distance 19 (FIG. FIG. 1 ) to the rotation axis 13, is arranged.
  • the rotary joint 16 is displaced so that it transmits no moment.
  • a pumping movement by entrainment by the crankshaft part 5 is omitted.
  • FIG. 3 shows a section through the internal combustion engine 1 with the subunits 2, 3 with coupled subunit 3 and thus coaxially arranged axes of rotation 12, 13.
  • the crankshaft parts 5, 6 are each axially fixed in the housing part 9 (FIGS. FIG. 1 ) or in the carriage 14 (FIG. FIG. 1 ) stored.
  • the connecting rods 4, 4a with the pistons 7, 7a are axially fixed in the Cranks 8 of the crankshaft parts 5, 6 with the same distance 19 between the axes of rotation 12 and 13 and the axes of rotation 20, 22 of the cranks 8 stored.
  • the rotational connection 16 is formed from the variable in its length eccentric 17 with the crank pin 23.
  • the crank pin 23 is rotatably received in the arranged at a distance 19 to the rotation axis 13 bearing bush 25 and positioned at affiliated subunit 3 with its axis of rotation 24 coaxial with the axis of rotation 22 of the connecting rod 4 a in the bearing bush 25 of the crankshaft part 6.
  • the Exzenterarm 17 is rotatably and coaxially connected to the crankshaft part 5 of the subunit 2, so that through the radially offset by the distance 19 arrangement between the rotation axis 12 of the crankshaft part 5 and the crank shaft part 6 mounted in the crank pin 23 of the Exzenterarms 17 torque on the rotary connection 16 can be transmitted and the two crankshaft parts are coaxially connected to each other rotationally.
  • the displaceable in the chamber 26 piston 27 is provided, wherein the chamber 26 is acted upon, for example by means of a rotary feedthrough with pressure medium and the piston 27 clamped against the eccentric 17. In this way, at the same time the axial compensation of the Exzenterarms be blocked.
  • FIG. 4 shows the upper arranged about the axis of rotation 13 of the subunit 3 part of the internal combustion engine 1 in the uncoupled from the subunit 2 subunit 3 in partial section.
  • the subunit 3 is so moved with its axis of rotation 13 relative to the axis of rotation 12 of the crankshaft part 5, that coincide with the axis of rotation 20 of the crank 8 axis of rotation 24 of the crank pin 23 and the bearing bush 25 for this coincide. Due to the coaxial arrangement of crankshaft part 5 and crank pin 23 no torque can be transmitted by means of the rotary connection 16, the crank pin 23 rotates with rotating crankshaft part 5 only in the bearing bush 25, the piston of the subunit 3, not shown, are therefore switched off.
  • FIG. 5 shows the internal combustion engine 1 with the subunits 2, 3 in section from below.
  • the rotary connection 16 with the eccentric 17 has a length compensation, which is designed as a linear guide 28 in the form of a dovetail joint 29.
  • These are in the camshaft part 5 and in the Exzenterarm 17 mutually complementary profiles provided with undercuts, which slide on each other and allow a rotational connection with radial displacement. In this way, while maintaining a rotational closure, a parallel displacement of the two crankshaft parts 5, 6 possible, the rotational closure connection 16 depending on the distance of the displacement, starting from the coaxial arrangement of the crankshaft parts 5, 6 to their maximum distance a decreasing, decreasing to the value zero Torque transfers.
  • FIG. 6 shows the internal combustion engine 1 with each other for clarity split subunits 2, 3 and the positioning of the rotary closure connection 16 in the coupled state of the two subunits 2, 3.
  • the coaxial arrangement of the axes of rotation 12, 13 of the crankshaft parts 5, 6 forces the eccentric 17 to a radial spaced position of the crank pin 23 with respect to the axes of rotation 12, 13, so that the non-rotatably and coaxially connected to the crankshaft part 6 flap member 30, which aligns the radially spaced from the axis of rotation 13, provided for receiving the journal 23 bearing bush 25 aligns accordingly.
  • Bushing 25 and crank pin 23 in this case form a rotary lever relative to the axes of rotation 12, 13 and thus transmit torque between the two crankshaft parts.
  • FIG. 6 shows the eccentric 17 radially to the crank pin 23 opposite a mass portion 31 in order to achieve a uniform moment of inertia in the coupled state of the subunits.
  • FIG. 7 shows in contrast to the representation of the internal combustion engine 1 in the FIG. 6
  • the parallel displacement of the axes of rotation 12, 13 of the crankshaft parts 5, 6 of the eccentric 17 is displaced radially outward and the crank pin 23 is displaced to the rotational axis 12 of the crankshaft part 5.

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

Claims (10)

  1. Moteur à combustion interne (1) constitué de plusieurs unités partielles (2, 3) comprenant respectivement une partie de vilebrequin (5, 6) sur laquelle est reçu respectivement au moins un piston (7, 7a) au moyen d'une bielle (4, 4a) sur un coude (8) de la partie de vilebrequin (5, 6), au moins une première unité partielle (2) fonctionnant en permanence pendant le fonctionnement du moteur à combustion interne (1) et au moins une unité partielle supplémentaire (3) pouvant être déconnectée, caractérisé en ce que les parties de vilebrequin (5, 6) de l'au moins une première unité partielle (2) et d'une deuxième unité partielle (3) adjacente pouvant être déconnectée sont reliées les unes aux autres de manière solidaire en rotation et peuvent être déplacées les unes par rapport aux autres par rapport à leurs axes de rotation (12, 13) de telle sorte qu'un mouvement de rotation appliqué à la partie de vilebrequin (6) de la deuxième unité partielle (3) par la partie de vilebrequin (5) de la première unité partielle (2) soit essentiellement supprimé.
  2. Moteur à combustion interne (1) selon la revendication 1, caractérisé en ce qu'un bras d'excentrique (17) pouvant être allongé en fonction du déplacement des parties de vilebrequin (5, 6) agit entre des parties de vilebrequin (5, 6) de la première et de la deuxième unité partielle (2, 3).
  3. Moteur à combustion interne (1) selon la revendication 2, caractérisé en ce que le bras d'excentrique (17) est réalisé de manière à pouvoir être allongé au moyen d'un guide linéaire (28).
  4. Moteur à combustion interne (1) selon la revendication 2 ou 3, caractérisé en ce que le bras d'excentrique (17) est disposé, sur l'une des parties de vilebrequin (5), sur son axe de rotation (12) et, sur l'autre partie de vilebrequin (6), essentiellement de manière décalée par rapport à l'axe de rotation (13) de la partie de vilebrequin (6) d'une distance correspondant à une distance (19) entre l'axe de rotation (13) de la partie de vilebrequin (6) et un axe de rotation (22) du coude (8) et disposé fixement sur l'une des parties de vilebrequin (5) et de manière rotative sur l'autre partie de vilebrequin (6).
  5. Moteur à combustion interne (1) selon l'une quelconque des revendications 2 à 4, caractérisé en ce que l'unité partielle (2) fonctionnant en permanence comprend une partie de vilebrequin (5) montée fixement par rapport à un boîtier (11) et la partie de vilebrequin (6) de l'unité partielle (3) pouvant être déconnectée peut être déplacée parallèlement à l'axe de rotation (12) de la partie de vilebrequin (5) de l'unité partielle (2) fonctionnant en permanence, la partie de vilebrequin (5) ne pouvant pas être déplacée recevant le bras d'excentrique (17) et la partie de vilebrequin (6) pouvant être déplacée étant reliée de manière solidaire en rotation à la partie de vilebrequin (5) ne pouvant pas être déplacée au moyen d'un maneton de bielle (23) prévu sur le bras d'excentrique (17), décalé radialement d'une certaine distance par rapport à l'axe de rotation (13) de la partie de vilebrequin (6) pouvant être déplacée et pouvant être déplacé radialement par rapport à l'axe de rotation (12) de la partie de vilebrequin ne pouvant pas être déplacée en fonction d'un déplacement de la partie de vilebrequin (6) pouvant être déplacée.
  6. Moteur à combustion interne (1) selon l'une quelconque des revendications 1 à 5, caractérisé en ce qu'une unité partielle (3) est disposée de manière à pouvoir être déplacée parallèlement par rapport à une autre unité partielle (2), par rapport à leurs axes de rotation (12, 13), au moyen d'un actionneur (15).
  7. Moteur à combustion interne (1) selon l'une quelconque des revendications 1 à 6, caractérisé en ce qu'une unité partielle (3) pouvant être déplacée est placée sur un chariot (14) disposé de manière à pouvoir être déplacé de manière limitée par rapport à un boîtier (11) comprenant l'unité partielle (2) ne pouvant pas être déplacée.
  8. Moteur à combustion interne (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce que, lorsque l'unité partielle (3) est déconnectée, le bras d'excentrique (17) présente un centre de gravité à l'extérieur de l'axe de rotation (12) de sa partie de vilebrequin (5).
  9. Moteur à combustion interne (1) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les parties de vilebrequin (5, 6) d'une unité partielle entraînée en permanence et d'une unité partielle connectée (2, 3) sont serrées axialement les unes contre les autres sans jeu.
  10. Moteur à combustion interne (1) selon l'une quelconque des revendications 7 à 9, caractérisé en ce que, lorsque l'unité partielle (3) est connectée, le boîtier (11) et le chariot (14) sont serrés sans jeu l'un contre l'autre.
EP11718894.6A 2010-03-22 2011-02-28 Moteur a combustion interne Not-in-force EP2550439B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010012279 2010-03-22
PCT/DE2011/000194 WO2011116737A1 (fr) 2010-03-22 2011-02-28 Moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2550439A1 EP2550439A1 (fr) 2013-01-30
EP2550439B1 true EP2550439B1 (fr) 2014-05-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11718894.6A Not-in-force EP2550439B1 (fr) 2010-03-22 2011-02-28 Moteur a combustion interne

Country Status (5)

Country Link
US (1) US8739758B2 (fr)
EP (1) EP2550439B1 (fr)
CN (1) CN102770642B (fr)
DE (2) DE102011012605A1 (fr)
WO (1) WO2011116737A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015213272A1 (de) * 2015-07-15 2017-01-19 Schaeffler Technologies AG & Co. KG Drehstarre Ausgleichskupplung und Vorrichtung mit einer solchen
FR3053421B1 (fr) * 2016-06-30 2020-02-28 Altran Technologies - Altran Dispositif d'accouplement en rotation
DE102016015112A1 (de) * 2016-12-20 2018-06-21 Deutz Aktiengesellschaft Brennkraftmaschine mit teilweiser Kolbenschränkung
CN109339945B (zh) * 2018-10-16 2020-09-22 杭州电子科技大学 一种基于正弦波抑制抵消的低脉动转矩内燃机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3017092A1 (de) * 1980-05-03 1981-11-05 Volkswagenwerk Ag, 3180 Wolfsburg Vorrichtung zur schaltbaren kupplung zweier wellenteile mit vorgegebener drehwinkelzuordnung
DE3145381A1 (de) 1981-11-14 1983-05-26 Volkswagenwerk Ag, 3180 Wolfsburg Mehrzylindrige hubkolben-brennkraftmaschine
US4555003A (en) * 1983-09-19 1985-11-26 Phillips Howard L Split engine clutch
DE19607920A1 (de) 1996-03-01 1997-09-04 Bayerische Motoren Werke Ag Hypozykloidisches Kurbelgetriebe für Hubkolbenmaschinen, insbesondere Brennkraftmaschinen
JP2008075561A (ja) * 2006-09-21 2008-04-03 Honda Motor Co Ltd 多気筒内燃機関
JP4616229B2 (ja) * 2006-09-29 2011-01-19 本田技研工業株式会社 多気筒内燃機関
EP2067961B1 (fr) 2007-12-05 2014-11-12 Volvo Car Corporation Dispositif de couplage

Also Published As

Publication number Publication date
WO2011116737A1 (fr) 2011-09-29
DE112011100986A5 (de) 2013-04-11
DE102011012605A1 (de) 2011-09-22
CN102770642A (zh) 2012-11-07
US8739758B2 (en) 2014-06-03
US20130014727A1 (en) 2013-01-17
EP2550439A1 (fr) 2013-01-30
CN102770642B (zh) 2015-10-21

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