EP3207233A1 - Groupe électrogène - Google Patents

Groupe électrogène

Info

Publication number
EP3207233A1
EP3207233A1 EP15770524.5A EP15770524A EP3207233A1 EP 3207233 A1 EP3207233 A1 EP 3207233A1 EP 15770524 A EP15770524 A EP 15770524A EP 3207233 A1 EP3207233 A1 EP 3207233A1
Authority
EP
European Patent Office
Prior art keywords
generator
toothed chain
chain
crankshafts
generator according
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.)
Granted
Application number
EP15770524.5A
Other languages
German (de)
English (en)
Other versions
EP3207233B1 (fr
Inventor
Franz Laimboeck
Frank Obrist
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.)
Obrist Technologies GmbH
Original Assignee
Obrist Technologies 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 Obrist Technologies GmbH filed Critical Obrist Technologies GmbH
Publication of EP3207233A1 publication Critical patent/EP3207233A1/fr
Application granted granted Critical
Publication of EP3207233B1 publication Critical patent/EP3207233B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/225—Multi-cylinder engines with cylinders in V, fan, or star arrangement having two or more crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/10—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with more than one main shaft, e.g. coupled to common output shaft
    • 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
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1808—Number of cylinders two
    • 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
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/04—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for electric generators
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/228—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders arranged in parallel banks

Definitions

  • the invention relates to a generator with the features of
  • the preamble of claim 1 Such a generator is known for example from WO 2012/056275 AI.
  • Spur gears are coupled to the shaft journal realized.
  • the spur gears engage with each other and synchronize the opposing crankshafts.
  • the generator is coupled to one of the two crankshafts by an idler gear meshing on one side with the spur gear of the crankshaft in question and on the other hand with another spur gear on the drive shaft of the generator.
  • the reciprocating engine of the known power generator already has excellent characteristics with regard to smoothness, low vibration and the compact design.
  • the generator is therefore preferably used for driving a hybrid vehicle.
  • the spur gear set of the two crankshafts is elaborately machined.
  • the invention is based on the object to improve the series suitability of the known power generator, without giving up the excellent engine characteristics, such as smoothness, low vibration and compactness.
  • the invention is further based on the object to provide a vehicle with such a generator.
  • the object is achieved by a generator with the features of claim 1 and by a vehicle having the features of claim 14.
  • the invention is based on the idea to propose a generator, in particular for a hybrid vehicle, which has a two-cylinder reciprocating engine and having a generator.
  • the two-cylinder reciprocating engine has two pistons, which are guided in two cylinders in tandem arrangement, and two counter-rotating crankshafts.
  • the crankshafts are connected to the pistons by connecting rods.
  • the generator is driven by the crankshaft, the crankshafts are mechanically coupled in phase.
  • the crankshafts are coupled by a toothed chain which is toothed on both sides, wherein the first side of the toothed chain engages with a sprocket of one crankshaft and the second side of the toothed chain engages with a sprocket of the other crankshaft.
  • the tooth chain and the crankshafts form a toothed chain drive, which coincides with the
  • the direction of rotation reversal of the two crankshafts is achieved by the toothed chain on both sides, so that the two crankshafts are synchronized.
  • the invention provides that the first side of the toothed chain with the one of the two sprockets and the second side of the toothed chain are in engagement with the other of the two sprockets.
  • the generator according to the invention is therefore suitable for series production in an advantageous manner.
  • toothed chain opens up various design possibilities, as the generator is spatially arranged with respect to the reciprocating engine.
  • the use of the double-sided toothed chain has the advantage that further engine components can be drive-connected to the crankshafts in a very simple and space-saving manner.
  • the specific embodiment of these engine components is the subject of the dependent claims.
  • the generator is arranged fixedly or interchangeably laterally next to the sprockets in a housing of the engine.
  • the reciprocating engine and the generator thus form a unit that in
  • Vehicle can be installed.
  • the replaceable arrangement of the generator improves the serviceability of the generator.
  • the generator and the toothed chain advantageously move in opposite directions during operation.
  • the generator is between a
  • Tensioning wheel and a guide wheel for the toothed chain arranged.
  • the first side of the toothed chain is in each case with the tensioning wheel and the guide wheel and the second side of the toothed chain with a drive pinion of the generator in engagement.
  • the arrangement of the generator between the tensioning and deflection wheel is particularly space-saving.
  • the direction of rotation reversal between the generator and the toothed chain is achieved in this embodiment in that one side of the toothed chain meshes with the tension wheel and the deflection wheel and the other side of the toothed chain meshes with the drive pinion of the generator.
  • the tensioning wheel enables automatic tensioning of the toothed chain. This can be done mechanically, for example by means of a spring, and / or hydraulically. Thus, with the help of an oil pump, a hydraulic pressure can be built up, which leads to a tension of the silent chain.
  • the automatic tensioning of the toothed chain optimizes the
  • Friction damping provided for the tensioning wheel.
  • the hydraulic damping can be operated by the oil pump.
  • the tensioning wheel can have a
  • two counterbalancing balance shafts are preferably connected to the silent chain, the first side of the silent chain meshing with a drive pinion of one balance shaft and the second side of the silent chain meshing with a drive pinion of the other balance shaft.
  • This coupling of the toothed chain with the balance shafts leads to a reversal of rotation of the two balance shafts, so that they rotate in opposite directions to each other.
  • Tooth chain front sprocket between 60 ° and 80 °, in particular between 65 ° and 75 °, a particularly good torque transfer between the silent chain and the sprocket is achieved. If the toothed chain forms a straight chain distance in the course between the sprockets of the crankshafts, which is at least approximately 30 mm, the running properties of the toothed chain, specifically the inlet of the toothed chain, are improved in the front sprocket in the direction of movement of the toothed chain. In the case of an ignition offset of 360 °, the situation arises that the crankshaft which is located in the running direction of the toothed chain is in the working stroke while the front crankshaft is in the intake stroke.
  • toothed chain is a Wiegezapfenkette.
  • a further reduction of the gas exchange torque and the load of the toothed chain drive is achieved in that the ignition interval is 0 ° crank angle. This applies in the event that the engine is a four-stroke engine.
  • the gas alternating torques of both cylinders occur at 0 ° Zündversatz at the same time and compensate each other because of the opposite movement of the crankshaft.
  • the stress on the chain drive becomes clear
  • each gear ratio of 1: 2 are available, so the drive pinion rotate at twice the speed. This concerns in particular the drive pinion of the balance shafts.
  • the cylinders are arranged parallel or inclined to each other with an inclination angle of 3 ° to 7 °, in particular 4 ° to 6 ° per cylinder.
  • the angle of inclination is measured between a vertical plane and the central axis of the respective cylinder. In other words, the total angle between the two cylinders is the sum of the inclination angles of the individual cylinders.
  • the parallel arrangement of the cylinder is structurally easy to implement.
  • the inclined arrangement has the advantage that the housing can be made compact in the cylinder area.
  • Cylinder centerlines in this case is smaller than the center distance of
  • the smoothness is further improved by the fact that the opposite direction to the generator rotating crankshaft has a larger flywheel than the same direction rotating to the generator crankshaft.
  • the single FIGURE shows a plan view of the front of a generator according to an embodiment of the invention.
  • the generator shown in the single figure is preferably, but not exclusively, used in a hybrid vehicle for charging the hybrid battery. Other applications where it depends on a quiet running, low-vibration and compact reciprocating engine, are possible.
  • the two pistons and the two cylinders which are guided in tandem arrangement.
  • the two counter-rotating crankshafts 10, 11 are drive-connected to the two pistons by connecting rods.
  • each crankshaft has its own piston-cylinder arrangement.
  • the cylinder center axes run in one and the same plane transverse to the crankshaft axes (tandem arrangement).
  • the two crankshafts are in opposite directions, ie they turn in the opposite direction. This is achieved by a corresponding arrangement of the crank pin and connecting rod in a conventional manner.
  • Synchronization of the two sprockets 12, 13 is a double-toothed chain 14 is provided, the first side with the first sprocket 12 and the second side with the second sprocket 13 is engaged. This reverses the direction of rotation.
  • One of the two sides of the toothed chain 14 may also be referred to as a spine.
  • the toothed chain 14 forms, together with the two crankshafts 10, 11, a sprocket drive which is connected to a generator 15. Together, the two-cylinder reciprocating engine and the generator 15, the power generator or power generator, the
  • a battery for example, for charging a battery, in particular for a hybrid drive, can be used.
  • the generator 15 is arranged in the same plane of rotation as the sprockets 12, 13, laterally beside them.
  • the axis of rotation of the generator 15 extends above the two crankshaft axes, which are arranged in one and the same horizontal plane.
  • the Genevatrum of the toothed chain 14 extends.
  • the coupling of the generator 15 with the toothed chain 14 is effected by a drive pinion 24, which sits on the generator drive shaft 21.
  • Drive pinion 24 is engaged with the same, in particular the first side of the toothed chain 14, as in the direction of movement of the toothed chain 14 front sprocket 12.
  • the generator drive shaft 21 and the first sprocket 12 thus rotate in the same direction. Accordingly, the generator drive shaft 21 and the rear in the direction of movement of the toothed chain 14 sprocket 13 rotate in opposite directions.
  • the generator 15 is arranged so that the Glastrum of the toothed chain 14 extends approximately horizontally between the drive pinion 24 of the generator 15 and the first sprocket 12. Another height position of the drive pinion 15 and the generator 15 relative to the crankshaft axes is possible. As can be seen in the single figure, the generator 15 and the
  • Reciprocating engine provided in the same housing 22 of the generator.
  • the generator 15 may be fixed or interchangeable in the housing 22.
  • connection of the generator 15 with the first side of the toothed chain 14 ensures that the generator 15 and the toothed chain 14 move in opposite directions during operation. In other words, the toothed chain 14 moves in the counterclockwise direction, whereas the generator 15 rotates clockwise.
  • the tensioning wheel 16 is adjustably mounted in the housing 22 in order to adjust the chain tension can.
  • the guide wheel 17 serves to guide the toothed chain 14 and is arranged upstream of the tensioning wheel 16 in the direction of movement of the toothed chain 14.
  • the tensioning wheel 16 is disposed below the drive shaft 21 of the generator and has a pinion which engages with the toothed chain 14.
  • the deflection wheel 17 is arranged above the drive shaft 21 of the generator and also has a pinion which engages with the toothed chain 14.
  • the tensioning wheel 16 and the guide wheel 17 are in each case with the other side of the toothed chain 14 as the generator 15 into engagement, resulting in the direction of rotation between the tensioning wheel 16 and the guide wheel 17 on the one hand and the generator 15 on the other. In other words rotate the tensioning wheel 16 and the guide wheel 17 and the rear in the direction of movement of the toothed chain 14 sprocket 13 in the same direction.
  • a guide rail can be provided for guiding a free chain length.
  • the tensioning wheel 16 and the guide wheel 17 are arranged offset one above the other.
  • the axial distance between the tensioning wheel 16 and the guide wheel 17 is dimensioned so that the drive shaft 21 of the generator in between
  • the tensioning wheel 16 is arranged below the horizontal plane through the two crankshaft axes and the deflection wheel 17 above this horizontal plane.
  • the guide wheel 17 is, relative to the tensioning wheel 16, arranged offset inwards, so that the toothed chain 14 between the Tensioning wheel 16 and the guide wheel 17 inwards in the direction of the two
  • the toothed chain 14 is connected to two counter-rotating balance shafts 18, 19.
  • the first side of the toothed chain 14 is connected to the drive pinion of the first balance shaft, i. the rear in the direction of movement of the toothed chain 14 balance shaft 18, connected.
  • the second side of the silent chain 14 is connected to the drive pinion of the second balance shaft 19, i. the front in the direction of movement of the toothed chain 14 balance shaft 19, connected. This results in the direction of rotation reversal of the two balance shafts 18, 19.
  • the two balance shafts 18, 19 are arranged in the Lostrum of the toothed chain 14. As can be seen in the single figure, the two balance shafts 18, 19 counterweights 23, which are arranged in-phase, but opposite directions. The balance shafts 18, 19 cooperate to balance the second-order mass forces.
  • the center distance between the two balance shafts 18, 19 is dimensioned so that there is space between them for the cylinder not shown in the single figure.
  • the toothed chain 14 extends straight between the first and second sprocket 12,
  • the toothed chain 14 is coupled to the second balance shaft 19 and extends from there under a change of the engagement side of the toothed chain 14 to the first balance shaft 18. From the first balance shaft 18th the toothed chain 14 continues to the guide roller 17, in which case again a change of the engagement side of the toothed chain and thus a
  • the pressure angle of the toothed chain 14 in all driving sprockets 12, 13 or the driven gears or pinions 15, 18, 19 is between 60 ° and 80 °, in particular between 65 ° and 75 °.
  • the gear ratio between the drive pinions 15, 18, 19 and the sprockets 11, 12 is 1: 2.
  • the double-sided toothed toothed chain has in a conventional manner toothed lugs, which engage in the corresponding teeth of the sprockets 12, 13 and take over the tensile force.
  • the cradle link of the silent chain has pivots or cradles that control the movement of the silent chain
  • tooth chains are well known.
  • the peculiarity of the above used toothed chain 14 is that the toothed chain is toothed on both sides.
  • Timing chain 26 the first crankshaft 10 with a camshaft sprocket 25 which is arranged on the front side of the camshaft.
  • the first crankshaft 10 has a chain pinion 27, which is fixedly connected to the first crankshaft 10 and / or the first sprocket 12.
  • the transmission ratio between the sprocket 27 and the camshaft sprocket 25 is in a conventional manner 1: 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

L'invention concerne un groupe électrogène, en particulier pour un véhicule hybride, qui comprend un moteur alternatif bicylindre comportant deux pistons guidés dans deux cylindres selon un agencement en tandem, et deux vilebrequins (10, 11) contrarotatifs qui sont reliés aux pistons par des bielles, et un générateur (15) qui est entraîné par les vilebrequins, les vilebrequins (10, 11) étant couplés mécaniquement de manière que leurs phases coïncident, les vilebrequins (10, 11) étant couplés par une chaîne dentée (14) à denture bilatérale, le premier côté de la chaîne dentée (14) s'engrenant avec un pignon (12) d'un vilebrequin (10) et le second côté de la chaîne dentée (14) s'engrenant avec un pignon (12) de l'autre vilebrequin (11), et la chaîne dentée (14) et les vilebrequins constituant une transmission à chaîne dentée qui est relié au générateur (15).
EP15770524.5A 2014-10-16 2015-09-28 Groupe électrogène Active EP3207233B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014115041.4A DE102014115041A1 (de) 2014-10-16 2014-10-16 Stromaggregat
PCT/EP2015/072195 WO2016058809A1 (fr) 2014-10-16 2015-09-28 Groupe électrogène

Publications (2)

Publication Number Publication Date
EP3207233A1 true EP3207233A1 (fr) 2017-08-23
EP3207233B1 EP3207233B1 (fr) 2018-09-26

Family

ID=54196967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15770524.5A Active EP3207233B1 (fr) 2014-10-16 2015-09-28 Groupe électrogène

Country Status (3)

Country Link
EP (1) EP3207233B1 (fr)
DE (1) DE102014115041A1 (fr)
WO (1) WO2016058809A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202018105331U1 (de) * 2018-02-26 2018-10-30 Obrist Technologies Gmbh Stromaggregat
JP7127889B2 (ja) * 2019-02-14 2022-08-30 株式会社石川エナジーリサーチ パワーユニット
DE102021100545A1 (de) * 2021-01-13 2022-07-14 Obrist Technologies Gmbh Verwendung eines global nutzbaren Energieträgers als Kraftstoff für ein Lastkraftfahrzeug oder einen Omnibus
DE102021122631A1 (de) 2021-09-01 2023-03-02 Obrist Technologies Gmbh Antriebssystem für ein Fahrzeug

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4285304A (en) * 1979-08-13 1981-08-25 Bachmann William V Internal combustion engine
DE3000531A1 (de) * 1980-01-09 1981-07-16 Erich 5421 Dachsenhausen Breitenbach Kolbenantriebsmaschien
DE3109908A1 (de) * 1981-03-14 1983-02-03 Ekkehard Dr.-Ing. 7100 Heilbronn Grau Schwingkolbenmaschine als kraft- und arbeitsmaschine und bausystem zur herstellung verschiedener maschinentypen (grau - motor)
US4470379A (en) * 1981-03-25 1984-09-11 Honda Giken Kogyo Kabushiki Kaisha Multi-cylinder engine
AU562848B2 (en) * 1984-03-15 1987-06-18 Honda Giken Kogyo Kabushiki Kaisha Multi-cylinder engine
AT5141U1 (de) * 2000-08-24 2002-03-25 Avl List Gmbh Viertakt-aussenbord-brennkraftmaschine zum antreiben eines wasserfahrzeuges
US7533639B1 (en) * 2007-10-29 2009-05-19 Ford Global Technologies, Llc Dual crankshaft engine with counter rotating inertial masses
CH703972A1 (de) 2010-10-29 2012-04-30 Obrist Engineering Gmbh Verbrennungskraftmaschine.
AT511552B1 (de) * 2011-05-30 2015-02-15 Avl List Gmbh Stromerzeuger für ein kraftfahrzeug

Also Published As

Publication number Publication date
WO2016058809A1 (fr) 2016-04-21
DE102014115041A1 (de) 2016-04-21
EP3207233B1 (fr) 2018-09-26

Similar Documents

Publication Publication Date Title
EP3025041B1 (fr) Groupe électrogène
EP3207232B1 (fr) Groupe électrogène
DE102009007465B3 (de) Antriebssystem für ein Walzwerk, insbesondere für ein Kaltpilgerwalzwerk
DE102014115043B4 (de) Stromaggregat
DE102018104546B3 (de) Stromaggregat
EP3207233B1 (fr) Groupe électrogène
EP1199452A1 (fr) Moteur à combustion interne, à rapport volumétrique variable, avec dispositif de réglage intégré
DE102006003026A1 (de) Wandelgetriebe, zur Umwandlung einer oszillierenden Bewegung in eine rotierende
DE19928416A1 (de) Ausgleichswelle für Verbrennungsmotoren
DE102010014218A1 (de) Drehkolbenpumpe und Verfahren zum Betreiben einer Drehkolbenpumpe
DE102010055584B4 (de) Vorrichtung zum Massenausgleich
DE2113193C3 (de) Vorrichtung zum Ausgleich der Massenkräfte zweiter Ordnung für Hubkolbenmaschinen
DE102008054335B4 (de) Dreh-Linear-Module Jura-DLM-EZ-A1
DE102020004112A1 (de) Verbundexzentergetriebe mit gekoppelten umlaufenden Wellen zur Umwandlung hin- und hergehender Bewegungen in eine kontinuierliche Drehbewegung und umgekehrt
DE102005025881A1 (de) Umschlingungstrieb
DE497588C (de) Kolbenmaschine, insbesondere Brennkraftmaschine, mit Hypozykloidengetriebe
EP3019770B1 (fr) Entraînement pourvu d'un moteur à piston et dispositif prévu pour un tel entraînement, et utilisation d'un tel dispositif pour la compensation de couples alternants
DE4441798A1 (de) Hubkolbenmaschine mit Massenausgleich
DE102018215118B3 (de) Antriebsvorrichtung, insbesondere nach Art eines Boxermotors
DE102015016703B4 (de) Verfahren zum Einstellen einer Zugmitteltriebanordnung
AT412804B (de) Getriebe für ein hubkolbenmotor- oder -pumpenaggregat
DE3907039A1 (de) Nockenwellenantrieb einer brennkraftmaschine
DE102021003329A1 (de) Verbundexzentergetriebe zur Umwandlung gerader hin- und hergehender Bewegungen in eine kontinuierliche Drehbewegung und umgekehrt im Sinusverhältnis
DE102007044162A1 (de) Hubkolbenmaschine
DE102014214188A1 (de) Kurbeltrieb für eine Hubkolben-Brennkraftmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20170511

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20180425

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1046302

Country of ref document: AT

Kind code of ref document: T

Effective date: 20181015

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502015006131

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181226

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181227

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181226

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

REG Reference to a national code

Ref country code: CH

Ref legal event code: PK

Free format text: BERICHTIGUNGEN

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

RIC2 Information provided on ipc code assigned after grant

Ipc: F01B 1/10 20060101ALI20160426BHEP

Ipc: B60K 6/24 20071001ALI20160426BHEP

Ipc: F02B 67/06 20060101AFI20160426BHEP

Ipc: F02B 75/22 20060101ALI20160426BHEP

Ipc: F02B 75/18 20060101ALI20160426BHEP

Ipc: F02B 63/04 20060101ALI20160426BHEP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190126

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190126

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180930

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502015006131

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180928

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180928

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180930

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180930

26N No opposition filed

Effective date: 20190627

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181126

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180926

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180926

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20150928

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190928

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190928

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1046302

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200928

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200928

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230929

Year of fee payment: 9